JP2019148284A - Oil supply device - Google Patents

Abstract

To provide an oil supply device capable of reducing loss of driving force for oil supply in a vehicle drive device.SOLUTION: An oil supply device 100 includes: a first oil-hydraulic pump 11 driven by driving force transmitted in a driving force transmission path; a second oil-hydraulic pump 12 driven by an electric motor 121; a first supply oil passage 31 supplying oil F to a lubrication object; a second supply oil passage 32 supplying oil pressure to engagement devices C0, C1; a first connection oil passage 41 connecting the first oil-hydraulic pump 11 and the first supply oil passage 31; a second connection oil passage 42 connecting the second oil-hydraulic pump 12 and the second supply oil passage 32; and a third oil passage 43 connecting the first connection oil passage 41 and the second connection oil passage 42, and provided with a first nonreturn valve 51 in the middle. A control valve 6 is provided at a downstream side of a first branch connection 41a. The control valve 6 makes oil pressure at an upstream side of the control valve 6 in the first connection oil passage 41 higher than oil pressure of the second connection oil passage 42, during the engagement operation of the engagement devices C0, C1.SELECTED DRAWING: Figure 2

Description

  The present invention includes a first driving force source that drives a wheel, a drive transmission mechanism that is provided in a power transmission path that connects the first driving force source and the wheel, and an engagement device that is provided in the power transmission path. And an oil supply device that supplies oil to a vehicle drive device.

  In Patent Document 1 below, a first driving force source (engine 1) that drives a wheel, and an engagement device (forward clutch) provided in a power transmission path that connects the first driving force source (engine 1) and the wheel. 12, a reverse clutch 13), and an oil supply device that supplies oil to a vehicle drive device is disclosed. The oil supply device of Patent Document 1 is driven by a first hydraulic pump (hydraulic pump 14) driven by a driving force transmitted through a power transmission path and a second driving force source (electric motor 111) independent of the power transmission path. A second hydraulic pump (second hydraulic pump 112). In addition, the member name and code | symbol shown in a parenthesis are the things of the patent document 1. FIG.

  In the oil supply device of Patent Document 1, in a steady state such as when the vehicle is running, the engagement device (forward clutch 12, reverse clutch 13) is driven from the first hydraulic pump (hydraulic pump 14) by the first driving force source (engine 1). Hydraulic pressure is supplied to On the other hand, the first driving force source (engine 1) is stopped due to a signal or the like, and the supply of hydraulic pressure from the first hydraulic pump (hydraulic pump 14) to the engagement devices (forward clutch 12 and reverse clutch 13) is stopped. , The second hydraulic pump (second hydraulic pump 112) driven by the second driving force source (electric motor 111) so that the engagement devices (forward clutch 12, reverse clutch 13) maintain the state immediately before engagement. ) Is supplied to the engaging devices (forward clutch 12 and reverse clutch 13).

  In the oil supply device of Patent Document 1, in a steady state such as when the vehicle is running, the first hydraulic pump (hydraulic pump 14) supplies hydraulic pressure to the engagement devices (forward clutch 12 and reverse clutch 13). Also, oil is supplied to lubrication objects such as gears. Therefore, the first hydraulic pump (hydraulic pump 14) has a comparatively high hydraulic pressure for engaging operation of the engaging devices (forward clutch 12 and reverse clutch 13) and a comparison for supplying lubricating oil to the lubrication target. It is necessary to secure a discharge amount that satisfies both a large flow rate. Therefore, in the oil supply apparatus of Patent Document 1, the capacity of the first hydraulic pump (hydraulic pump 14) must be increased, and the loss of driving force due to driving the first hydraulic pump (hydraulic pump 14) is large. There was a problem of becoming.

JP-A-11-93721 (paragraphs 0020, 0023 and FIG. 3)

  Therefore, it is desired to realize an oil supply device that can suppress a loss of driving force for oil supply in the vehicle drive device.

In view of the above, the characteristic configuration of the oil supply device is as follows:
A first driving force source for driving a wheel; a drive transmission mechanism provided in a power transmission path connecting the first driving force source and the wheel; and an engagement device provided in the power transmission path. An oil supply device for supplying oil to a vehicle drive device,
A first hydraulic pump driven by a driving force transmitted through the power transmission path;
A second hydraulic pump driven by a second driving force source independent of the power transmission path;
A first supply oil passage for supplying lubricating oil to a lubrication target including the drive transmission mechanism;
A second supply oil path for supplying control hydraulic pressure to the engagement device;
A first connection oil passage connecting the first hydraulic pump and the first supply oil passage;
A second connection oil passage connecting the second hydraulic pump and the second supply oil passage;
Connecting the first connection oil passage and the second connection oil passage, and a third connection oil passage provided with a first check valve in the middle,
The first check valve regulates the flow of oil from the second connection oil passage side to the first connection oil passage side,
A control valve for controlling the hydraulic pressure of the first connection oil passage is provided on the downstream side of the connection portion with the third connection oil passage in the first connection oil passage,
During the engagement operation for changing the engagement device from the disengaged state to the engaged state, the control valve applies a hydraulic pressure upstream of the control valve in the first connection oil passage to a hydraulic pressure in the second connection oil passage. It is in the point which performs control during engagement operation made higher than.

According to this characteristic configuration, in a steady state other than during the engagement operation of the engagement device, the first hydraulic pump supplies lubricating oil to the lubrication target, and the second hydraulic pump is directed to the engagement device. Supply hydraulic pressure for control. Therefore, compared with the configuration in which the first hydraulic pump supplies both the lubricating oil supplied to the lubrication target and the control hydraulic pressure supplied to the engagement device, the discharge hydraulic pressure required for the first hydraulic pump is reduced. The maximum value can be kept low. Therefore, the enlargement of the first hydraulic pump can be suppressed, and the loss of the driving force of the vehicle drive device caused by driving the first hydraulic pump can be suppressed to a low level.
Further, in the steady state as described above, the flow rate of oil supplied for controlling the engagement device is small, so that the discharge flow rate required for the second hydraulic pump can also be kept small. According to this configuration, during the engagement operation that changes the engagement device from the released state to the engaged state, the control valve is controlled to engage the first hydraulic pump via the third connection oil passage. Supply hydraulic pressure for control to the combined device. For this reason, the second hydraulic pump does not need to supply the hydraulic pressure necessary for the engagement operation of the engagement device, as long as it can supply the hydraulic pressure for maintaining the engagement state of the engagement device in the steady state. Therefore, the maximum value of the discharge hydraulic pressure required for the second hydraulic pump can be kept low. Therefore, the enlargement of the second hydraulic pump can be suppressed.

The figure which shows schematic structure of the drive device for vehicles provided with the oil supply apparatus which concerns on 1st Embodiment. The figure which shows the oil supply apparatus which concerns on 1st Embodiment. The figure which shows the flow of the oil in the steady state in the oil supply apparatus which concerns on 1st Embodiment. The figure which shows the flow of the oil during engagement operation of the engagement apparatus in the oil supply apparatus which concerns on 1st Embodiment. The figure which shows the relationship between the hydraulic pressure and flow volume of the oil which the 1st hydraulic pump and 2nd hydraulic pump of the oil supply apparatus which concern on 1st Embodiment discharge. The figure which shows the oil supply apparatus which concerns on 2nd Embodiment. The figure which shows the relationship between the hydraulic pressure and the flow volume of the oil which the 1st hydraulic pump and 2nd hydraulic pump of the oil supply apparatus which concern on 2nd Embodiment discharge.

1. First Embodiment Hereinafter, an oil supply apparatus 100 according to a first embodiment will be described with reference to the drawings. The oil supply device 100 is a device that supplies oil F to the vehicle drive device D.
In this specification, “rotary electric machine” is used as a concept including any of a motor (electric motor), a generator (generator), and a motor / generator that functions as both a motor and a generator as necessary. Yes.
Further, in this specification, “drive connection” refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, It includes a state in which two rotating elements are connected to each other through one or more transmission members so as to be able to transmit a driving force. Such transmission members include various members (shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at different speeds, and an engagement device that selectively transmits rotation and driving force. (Such as a friction engagement device or a meshing engagement device) may be included.

  As shown in FIG. 1, the vehicle drive device D includes an input shaft I, an intermediate shaft M, an output shaft O, a starting engagement device C0, a rotating electrical machine MG, a transmission TM, and a counter gear mechanism. G and a differential gear device DF. The starting engagement device C0, the rotating electrical machine MG, the transmission TM, the counter gear mechanism G, and the differential gear device DF are described from the internal combustion engine EN side to the power transmission path P that connects the internal combustion engine EN and the wheels W. Arranged in order. These are housed in a case (not shown).

  The input shaft I is connected so as to rotate integrally with the output shaft (crankshaft or the like) of the internal combustion engine EN, or the output shaft of the internal combustion engine EN via another member such as a damper or a fluid coupling (torque converter or the like). It is connected to the drive.

  The internal combustion engine EN is a prime mover (gasoline engine, diesel engine, etc.) that is driven by the combustion of fuel inside the engine to extract power. In the present embodiment, the internal combustion engine EN corresponds to one of the “first driving force sources” that drives the wheels W.

  The rotating electrical machine MG includes a stator St fixed to the case, and a rotor Ro that is rotatably supported with respect to the stator St. In the present embodiment, the rotor Ro is disposed on the inner side in the radial direction of the stator St and is drivingly connected so as to rotate integrally with the intermediate shaft M. In the present embodiment, the rotating electrical machine MG corresponds to one of the “first driving force sources” that drives the wheels W. In the present embodiment, the rotating electrical machine MG is supplied with lubricating and cooling oil F via a first lubricating oil passage 311 described later. The oil F supplied via the first lubricating oil passage 311 lubricates the operating parts of the rotating electrical machine MG and cools the heat generating parts of the stator St and the rotor Ro. Thereafter, the oil F is discharged to the outside of the rotating electrical machine MG, and the oil F is returned to the oil reservoir S (see FIG. 2). The oil storage part S is comprised by the oil pan etc. which were provided in the bottom part of the case, for example.

  The starting engagement device C0 is interposed between the input shaft I and the intermediate shaft M. In the engaged state of the starting engagement device C0, power is transmitted between the input shaft I and the intermediate shaft M, and in the released state of the starting engagement device C0, between the input shaft I and the intermediate shaft M. Is interrupted. In the present embodiment, the starting engagement device C0 includes an input side engagement member that is drivingly connected to the input shaft I, and an output side engagement member that is drivingly connected to the rotor Ro of the rotating electrical machine MG. . The starting engagement device C0 corresponds to one of the “engagement devices” provided in the power transmission path P.

  Here, the “engaged state” of the engagement device is a state where a transmission torque capacity is generated in the engagement device. In the “engagement state”, there is a “direct engagement state” in which there is no rotational speed difference between the engagement members of the engagement device, and a “sliding engagement state” in which there is a rotation speed difference between the engagement members of the engagement device. And are included. Further, the “released state” of the engaging device is a state where no transmission torque capacity is generated in the engaging device. When the engagement device is a friction engagement device, the transmission torque capacity is generated by dragging between the engagement members (friction members) even if a command for generating the transmission torque capacity is not issued by the control device. There is. In the present specification, a state where the transmission torque capacity is generated by the dragging when the instruction for generating the transmission torque capacity is not issued is also included in the “released state”.

  The starting engagement device C0 is a hydraulically driven engagement device including a first hydraulic servo mechanism 81 (see FIG. 2) that operates in accordance with the supplied hydraulic pressure. In the present embodiment, the starting engagement device C0 is a friction engagement device that transmits torque by the frictional force generated between the engaging members that are engaged with each other, and specifically, a wet multi-plate clutch mechanism. A wet friction engagement device provided. The first hydraulic servomechanism 81 includes an operating hydraulic chamber (not shown) to which oil F for controlling the engagement state is supplied. Oil F is supplied to the hydraulic pressure chamber via a first control oil passage 321 described later. The state of engagement of the starting engagement device C0 is controlled by controlling the hydraulic pressure in the working hydraulic chamber by a first engagement control valve 71 described later.

  In this embodiment, lubricating oil F and cooling oil F are supplied to the starting engagement device C0 via a second lubricating oil passage 312 described later. The engagement member of the starting engagement device C0 is lubricated and cooled by the oil F supplied through the second lubricating oil passage 312. Thereafter, the oil F is discharged to the outside of the starting engagement device C0, and the oil F is returned to the oil reservoir S (see FIG. 2).

  The transmission TM is a device that shifts the rotation of the transmission input shaft and transmits it to the output shaft O. In the present embodiment, the transmission TM is configured such that the gear ratio can be changed stepwise or continuously. Then, the transmission TM changes the rotational speed of the intermediate shaft M at the current speed ratio and transmits it to the counter gear mechanism G. In the present embodiment, the transmission TM includes a plurality of shift engagement devices C1, and the gear position is switched by controlling the engagement state of each of the plurality of shift engagement devices C1. The plurality of shift engagement devices C1 include at least one of a clutch and a brake. As the transmission TM, for example, various known transmissions such as a stepped automatic transmission, a continuously variable automatic transmission, and a manual transmission can be used. 1 and 2 show only one of the plurality of shift engagement devices C1.

  In the present embodiment, lubricating and cooling oil F is supplied to the transmission TM via a third lubricating oil passage 313 described later. The oil supplied through the third lubricating oil passage 313 lubricates and cools the gearshift engagement device C1, the gear mechanism, the bearing, and the like included in the transmission TM. Thereafter, the oil F is discharged to the outside of the transmission TM, and the oil F is returned to the oil reservoir S (see FIG. 2).

  The shift engagement device C1 is a hydraulically driven engagement device including a second hydraulic servo mechanism 82 (see FIG. 2) that operates in accordance with the supplied hydraulic pressure. The shift engagement device C1 corresponds to one of the “engagement devices” provided in the power transmission path P. In the present embodiment, the shift engagement device C1 is a friction engagement device that transmits torque by the frictional force generated between the engagement members that are engaged with each other, and specifically, a wet multi-plate clutch mechanism. A wet friction engagement device provided. The second hydraulic servo mechanism 82 includes an operating hydraulic chamber (not shown) to which oil F for controlling the engagement state is supplied. Oil F is supplied to the hydraulic pressure chamber via a second control oil passage 322 described later. By controlling the hydraulic pressure of the working hydraulic chamber by a second engagement control valve 72 described later, the state of engagement of the shift engagement device C1 is controlled.

  The counter gear mechanism G is a gear mechanism disposed between the transmission TM and the differential gear device DF in the power transmission path P. The counter gear mechanism G is drivingly connected to the two output shafts O via the differential gear device DF. Therefore, the rotation and torque transmitted from the transmission TM side to the counter gear mechanism G are distributed and transmitted to the two output shafts O (two wheels W) via the differential gear device DF. Accordingly, the vehicle drive device D can cause the vehicle to travel by transmitting the torque of one or both of the internal combustion engine EN and the rotating electrical machine MG to the wheels W. That is, the vehicle drive device D is configured as a drive device for a hybrid vehicle, and specifically, is configured as a one-motor parallel type hybrid drive device.

  In the present embodiment, lubricating oil F is supplied to the counter gear mechanism G via a fourth lubricating oil passage 314 described later. The counter gear mechanism G is lubricated by the oil supplied through the fourth lubricating oil passage 314. Thereafter, the oil F is discharged to the outside of the counter gear mechanism G, and the oil F is returned to the oil reservoir S (see FIG. 2).

  In the present embodiment, lubricating oil F is supplied to the differential gear unit DF via a fifth lubricating oil passage 315 described later. The differential gear device DF is lubricated by the oil supplied through the fifth lubricating oil passage 315. Thereafter, the oil F is discharged to the outside of the differential gear device DF, and the oil F is returned to the oil reservoir S (see FIG. 2).

  As shown in FIG. 1, the oil supply device 100 includes a first hydraulic pump 11 and a second hydraulic pump 12. The first hydraulic pump 11 and the second hydraulic pump 12 are hydraulic pumps that discharge the oil F. As the first hydraulic pump 11 and the second hydraulic pump 12, for example, an internal or external gear pump, a vane pump, or the like can be employed.

  The first hydraulic pump 11 is a mechanical hydraulic pump that is driven by a driving force transmitted through the power transmission path P. In the illustrated example, the first hydraulic pump 11 is disposed on a different shaft from the input shaft I and the rotating electrical machine MG, and the drive shaft 11a of the first hydraulic pump 11 is an intermediate shaft M via a sprocket and a chain. It is drive-coupled to rotate in conjunction with. Note that the first hydraulic pump 11 may be arranged coaxially with the input shaft I and the rotating electrical machine MG.

  The second hydraulic pump 12 is an electric hydraulic pump that is driven by an electric motor 121 independent of the power transmission path P. In the present embodiment, the second hydraulic pump 12 is configured to be able to control the discharge pressure of the oil F. Specifically, the electric motor 121 is controlled by the control device 10 described later so that the discharge pressure of the oil F from the second hydraulic pump 12 becomes a target value. Note that the discharge flow rate of the oil F from the second hydraulic pump 12 may be controlled by controlling the electric motor 121. Such control of the second hydraulic pump 12 is performed by controlling at least one of the rotational speed and torque of the electric motor 121.

  The electric motor 121 corresponds to a “second driving force source” independent of the power transmission path P. As the electric motor 121, for example, an AC rotating electric machine driven by a plurality of phases of AC power can be used. In this case, although not shown, the electric motor 121 is connected to a DC power source via an inverter that converts power between DC power and AC power, and the control device 10 is connected to the electric motor via the inverter. The drive of 121 is controlled. In the present embodiment, the electric motor 121 is a rotating electrical machine that is smaller than the rotating electrical machine MG for driving the wheels W. Therefore, the electric motor 121 has a smaller maximum torque value that can be output than the rotating electrical machine MG or the internal combustion engine EN.

  As shown in FIG. 2, the first hydraulic pump 11 and the second hydraulic pump 12 are connected to a strainer 23 via a first suction oil passage 21 and a second suction oil passage 22, respectively. Specifically, the first suction oil passage 21 is connected to the suction port of the first hydraulic pump 11, and the second suction oil passage 22 is connected to the suction port of the second hydraulic pump 12. And the 1st suction oil path 21 and the 2nd suction oil path 22 have joined, and the strainer 23 is connected to the downstream rather than the junction. The strainer 23 is a filter that removes foreign matter contained in the oil F when the first hydraulic pump 11 or the second hydraulic pump 12 sucks the oil F stored in the oil storage section S. Oil F after being circulated through each part of the vehicle drive device D is stored in the oil storage part S. The first intake oil passage 21 and the second intake oil passage 22 may not be joined, and the strainer 23 may be connected to each of the first intake oil passage 21 and the second intake oil passage 22.

  The oil supply device 100 includes a first supply oil passage 31, a second supply oil passage 32, a first connection oil passage 41, a second connection oil passage 42, and a third connection oil passage 43. ing.

  The first supply oil passage 31 is an oil passage for supplying the lubricating oil F to the lubrication target L including the drive transmission mechanism T. In the present embodiment, the first supply oil passage 31 includes the first lubricant oil passage 311, the second lubricant oil passage 312, the third lubricant oil passage 313, the fourth lubricant oil passage 314, and the fifth lubricant oil passage. 315. As described above, these oil passages are formed so that oil F can be supplied to the rotating electrical machine MG, the starting engagement device C0, the transmission TM, the counter gear mechanism G, and the differential gear device DF, respectively. . Therefore, in the present embodiment, the lubrication target L includes the rotating electrical machine MG, the starting engagement device C0, the transmission TM, the counter gear mechanism G, and the differential gear device DF. In the present embodiment, the drive transmission mechanism T includes the rotor shaft of the rotating electrical machine MG, the starting engagement device C0, the shifting engagement device C1 of the transmission TM, the gear mechanism, the counter gear mechanism G, and the difference. The gear mechanism of the dynamic gear device DF and the like are included.

  The second supply oil passage 32 is an oil passage for supplying hydraulic pressure for control to the starting engagement device C0 and the shifting engagement device C1. In the present embodiment, the second supply oil passage 32 includes a first control oil passage 321 and a second control oil passage 322. As described above, the first control oil passage 321 is connected to the first hydraulic servo mechanism 81 of the starting engagement device C0, and the second control oil passage 322 is connected to the second hydraulic servo mechanism 82 of the transmission engagement device C1. The oil F can be supplied.

  The first connection oil passage 41 is an oil passage that connects the first hydraulic pump 11 and the first supply oil passage 31. The second connection oil passage 42 is an oil passage that connects the second hydraulic pump 12 and the second supply oil passage 32. The third connection oil passage 43 is an oil passage that connects the first connection oil passage 41 and the second connection oil passage 42. In this embodiment, the connection part with the 3rd connection oil path 43 in the 1st connection oil path 41 is called the 1st branch part 41a. Further, the connection portion of the second connection oil passage 42 with the third connection oil passage 43 is referred to as a second branch portion 42a.

  A first check valve 51 is provided in the middle of the third connection oil passage 43. The first check valve 51 is a valve that regulates the flow of the oil F from the second connection oil passage 42 side to the first connection oil passage 41 side. In the present embodiment, the second check valve 52 is provided on the upstream side of the second branch portion 42 a in the second connection oil passage 42. The second check valve 52 is a valve that regulates the flow of the oil F from the second branch portion 42a side to the second hydraulic pump 12 side.

  A control valve 6 that controls the hydraulic pressure of the first connection oil passage 41 is provided downstream of the first branch portion 41a. In the following description, for the sake of convenience, the upstream portion of the first connection oil passage 41 with respect to the control valve 6 is referred to as an upstream portion 411, and the downstream portion of the control valve 6 is referred to as a downstream portion 412.

  In the present embodiment, the control valve 6 is configured to control the hydraulic pressure of the upstream portion 411. In the illustrated example, the control valve 6 adjusts the hydraulic pressure using the hydraulic pressure supplied from the command pressure control valve 61 as a signal pressure. The command pressure control valve 61 is controlled by the control device 10 described later so as to output a hydraulic pressure (signal pressure) corresponding to the target hydraulic pressure. Here, a linear solenoid valve is used as the command pressure control valve 61. The control valve 6 includes a sleeve in which a plurality of ports are formed, and a spool (valve element) that slides inside the sleeve. The sleeve receives an input port 6 a connected to the upstream portion 411, an output port 6 b connected to the downstream portion 412, a discharge port 6 c connected to a return oil passage 62 described later, and a signal pressure from the command pressure control valve 61. A signal pressure input port (not shown) to be supplied, a feedback port (not shown) that is an inlet to the feedback hydraulic chamber, and the like are provided. The position of the spool moves according to the balance between the hydraulic pressure supplied to the feedback hydraulic chamber and the signal pressure supplied from the command pressure control valve 61, and the communication between different ports depends on the position of the spool. Is changed, the hydraulic pressure of the upstream portion 411 or the downstream portion 412 is adjusted. In the present embodiment, the same hydraulic pressure as that of the upstream portion 411 is supplied to the feedback port, whereby the hydraulic pressure of the upstream portion 411 is controlled according to the signal pressure.

  In the present embodiment, the control valve 6 has a discharge port 6 c connected to the return oil passage 62, and is configured to discharge drain oil accompanying the adjustment of the hydraulic pressure to the return oil passage 62. The return oil path 62 is an oil path that connects the discharge port 6 c of the control valve 6 to the first suction oil path 21 that is connected to the suction port of the first hydraulic pump 11. In the present embodiment, the return oil passage 62 is connected to the downstream side of the joining portion of the first suction oil passage 21 and the second suction oil passage 22 and to the upstream side of the strainer 23.

  In the present embodiment, the second connection oil passage 42 is not provided with a hydraulic control valve that controls the oil pressure of the second connection oil passage 42. However, this does not exclude providing a relief valve in the second connection oil passage 42. The relief valve for releasing the hydraulic pressure when excessive hydraulic pressure is generated in the second connection oil passage 42 does not actively control the hydraulic pressure in the second connection oil passage 42, but is a hydraulic control valve here. Is not included. The second connection oil passage 42 may be provided with a hydraulic control valve that controls the oil pressure of the second connection oil passage 42 without being limited to such a configuration.

  The first control oil path 321 is connected to the first hydraulic servo mechanism 81 via the first engagement control valve 71. The first engagement control valve 71 is controlled by the control device 10, adjusts the hydraulic pressure of the first control oil passage 321 in accordance with the applied current, and supplies it to the first hydraulic servo mechanism 81 of the starting engagement device C0. To do. The second control oil passage 322 is connected to the second hydraulic servo mechanism 82 via the second engagement control valve 72. The second engagement control valve 72 is controlled by the control device 10, adjusts the hydraulic pressure of the second control oil passage 322 in accordance with the applied current, and supplies it to the second hydraulic servo mechanism 82 of the shift engagement device C1. To do. In the present embodiment, the same number of the second hydraulic servo mechanisms 82 as the shift engagement devices C1 are provided. In FIG. 2, one of them is representatively shown, and the one second hydraulic servo mechanism 82 is shown. Only the second engagement control valve 72 for supplying hydraulic pressure is shown. Note that the number of second engagement control valves 72 may be smaller than that of the shift engagement device C1. In this case, an oil path switching mechanism (oil path switching valve) that switches the hydraulic pressure supply destination between the plurality of shift engagement devices C1 (a plurality of hydraulic servo mechanisms) downstream of the second engagement control valve 72. Is provided.

  As shown in FIG. 2, the oil supply device 100 includes a control device 10. As described above, the control device 10 is electrically connected to and controls the electric motor 121, the command pressure control valve 61, the first engagement control valve 71, and the second engagement control valve 72.

  The control device 10 includes an arithmetic processing device such as a CPU (Central Processing Unit) as a core member, and also includes a storage device such as a RAM (Random Access Memory) and a ROM (Read Only Memory) that can be referred to by the arithmetic processing device. ing. Each function of the control device 10 is realized by software (program) stored in a storage device such as a ROM, hardware such as a separately provided arithmetic circuit, or both. The control device 10 is configured to communicate with each other with an integrated control device (not shown) that controls the vehicle as a whole, and the control device 10 and the integrated control device communicate various information. It is configured to share and perform cooperative control. In addition to the control device 10, this integrated control device communicates with the rotating electrical machine control device that controls the operation of the rotating electrical machine MG and the internal combustion engine control device that controls the operation of the internal combustion engine EN. It is configured. Further, the integrated control device is configured to be able to acquire information on detection results from various sensors (for example, accelerator opening, vehicle speed sensor, oil temperature sensor, etc.) provided in the vehicle. At least a part of the control device 10 may constitute a part of the integrated control device.

  FIG. 3 shows the flow of the oil F in the steady state in the oil supply apparatus 100. As shown in FIG. 3, in the steady state, the first hydraulic pump 11 discharges the oil F so that the oil F flows into the first supply oil passage 31 via the first connection oil passage 41. At this time, the control valve 6 performs control so that the oil F having the flow rate Q1 flows in the upstream portion 411 of the first connection oil passage 41 with the hydraulic pressure P1. As described above, the second hydraulic pump 12 is configured to be able to control the discharge pressure of the oil F, and discharges the oil F so that the oil F having a flow rate Q2 flows through the second connection oil passage 42 at the oil pressure P2. At this time, the hydraulic pressure P1 of the upstream portion 411 of the first connection oil passage 41 is lower than the hydraulic pressure P2 of the second connection oil passage 42. Therefore, the first check valve 51 is closed, and the oil F flowing through the first connection oil passage 41 does not flow into the second connection oil passage 42 via the third connection oil passage 43 (FIG. 3). (See arrow F along the first connecting oil passage 41). Further, the oil F flowing through the second connection oil passage 42 is flowed from the second connection oil passage 42 to the first connection oil passage 41 by the first check valve 51 provided in the third connection oil passage 43. It is regulated (see arrow F along the second connection oil passage 42 in FIG. 3). Therefore, the oil F flowing through the second connection oil passage 42 is supplied to the second supply oil passage 32 (see arrow F along the second connection oil passage 42 in FIG. 3). Note that the flow rate Q1 of the upstream portion 411 of the first connection oil passage 41 is larger than the flow rate Q2 of the second connection oil passage 42. Then, the control valve 6 performs control so that the flow rate of the downstream portion 412 of the first connection oil passage 41 becomes an amount suitable for the lubrication of the lubrication target L.

Here, the “steady state” is a state other than during the engagement operation in which the engagement devices C0 and C1 are changed from the released state to the engaged state. Such a “steady state” includes a state in which at least all of the engagement devices C0 and C1 do not change state, for example, includes a state in which the vehicle is traveling at a constant shift speed.
In FIG. 3, for convenience, illustration of some elements in the oil supply apparatus 100 is omitted, and this is the same in FIG. 4.

  FIG. 4 shows the flow of the oil F during the engagement operation of the engagement devices C0 and C1 in the oil supply device 100. As shown in FIG. 4, the control valve 6 causes the hydraulic pressure P1 of the upstream portion 411 of the first connection oil passage 41 to be greater than the hydraulic pressure P2 of the second connection oil passage 42 during the engagement operation of the engagement devices C0 and C1. Engagement-in-operation control is performed so that the engagement-in-operation oil pressure P1U is high. Specifically, during the engagement operation of the engagement devices C0 and C1, the control device 10 controls the command pressure control valve 61 so that the hydraulic pressure of the oil F flowing in the upstream portion 411 becomes the hydraulic pressure P1U during the engagement operation. To do. Thereby, the control valve 6 restrict | squeezes the flow volume of the oil F which flows into the downstream part 412 from the upstream part 411 of the 1st connection oil path 41, and reduces the flow volume of the oil F of the downstream part 412 from the flow volume in a steady state. . Here, since the first hydraulic pump 11 is driven by a sufficiently large driving force by the internal combustion engine EN and the rotating electrical machine MG that are the driving force sources of the wheels W, the oil F that flows in the upstream portion 411 that is the discharge destination When the flow rate is limited, the hydraulic pressure in the upstream portion 411 is increased. As a result, the hydraulic pressure P1 of the upstream portion 411 becomes the engaging hydraulic pressure P1U that is higher than the hydraulic pressure P2 of the second connection oil passage 42. Further, the flow rate Q1 of the upstream portion 411 decreases to the flow rate Q1D during the engaging operation that is smaller than the steady state. Accordingly, the oil F flows from the first connection oil passage 41 to the second connection oil passage 42 via the third connection oil passage 43 (see arrow F in FIG. 4).

  In the present embodiment, the control valve 6 is configured such that, during the engaging operation of the engaging devices C0 and C1, the hydraulic pressure downstream of the second branch oil passage 42a in the second connection oil passage 42 is greater than the hydraulic pressure necessary for the engaging operation. The control during the engaging operation is executed so that That is, the hydraulic pressure P1U during the engagement operation is set to a higher hydraulic pressure than the maximum hydraulic pressure required for the engagement operation of the engagement devices C0 and C1. Thereby, engagement operation of engagement device C0 and C1 can be performed appropriately.

  In the present embodiment, as described above, the control valve 6 reduces the flow rate of the oil F in the downstream portion 412 of the first connection oil passage 41 from the flow rate in the steady state during execution of the control during the engagement operation. . Thereby, during execution of control during engagement operation, the flow rate of the oil F in the 1st supply oil path 31 becomes lower than the required flow rate in a steady state. According to this configuration, the first hydraulic pump that supplies both the hydraulic pressure for controlling the engagement devices C0 and C1 and the lubricating oil F for the lubrication target L during execution of the control during the engagement operation. 11 can be kept relatively small. Therefore, the enlargement of the first hydraulic pump 11 can be suppressed, and the driving force required to drive the first hydraulic pump 11 can be suppressed to a small value. Even if the flow rate of the lubricating oil F supplied to the lubrication target L is lower than the required flow rate in the steady state, the lubrication oil exists in various places on the lubrication target L, and therefore the engaging operation is in progress. Problems due to a temporary decrease in the flow rate are unlikely to occur.

  In the present embodiment, the second hydraulic pump 12 reduces the discharge pressure during the engagement operation of the engagement devices C0 and C1. Specifically, during the engagement operation of the engagement devices C0 and C1, that is, during the execution of the control during the engagement operation by the control valve 6, the second connection oil passage 42 is upstream of the second check valve 52. The hydraulic pressure P2 of the oil F is lowered to the hydraulic pressure P2D, and the flow rate Q2 of the oil F flowing upstream from the second check valve 52 in the second connection oil passage 42 is reduced to the reduced flow rate Q2D. The apparatus 10 controls the electric motor 121. During the engagement operation of the engagement devices C0 and C1, even if the oil F is discharged from the second hydraulic pump 12, it is not supplied to the engagement devices C0 and C1. Therefore, by reducing the discharge pressure and the discharge flow rate of the second hydraulic pump 12, energy consumption in the electric motor 121 that drives the second hydraulic pump 12 can be reduced, and the load acting on the second hydraulic pump 12. Can be reduced. From the viewpoint of energy efficiency, it is preferable to stop the electric motor 121 and set the post-reduction hydraulic pressure P2D and the post-decrease flow rate Q2D to zero. Alternatively, when the engagement operation of the engagement devices C0 and C1 is finished and the supply of the oil F from the second hydraulic pump 12 to the second supply oil passage 32 is resumed, the discharge hydraulic pressure of the second hydraulic pump 12 rises. In order to suppress this delay, it is also preferable to maintain the post-drop hydraulic pressure P2D and the post-drop hydraulic flow Q2D at values greater than zero.

  When the engagement operation of the engagement devices C0 and C1 is finished, the control valve 6 finishes the control during the engagement operation. That is, the control valve 6 reduces the hydraulic pressure of the upstream portion 411 of the first connection oil passage 41 from the engaging operation hydraulic pressure P1U to the steady state hydraulic pressure P1, and the flow rate from the engaging operation flow rate Q1D to the steady state flow rate Q1. Increase to. Thereby, the flow rate of the oil F in the downstream part 412 of the 1st connection oil path 41 and the 1st supply oil path 31 increases, and the oil F of the flow volume required in the steady state is supplied with respect to the lubrication object L, Become. Further, the second hydraulic pump 12 increases the discharge pressure and returns to the state in which the oil F is discharged so that the oil F at the flow rate Q2 flows in the second connection oil passage 42 at the oil pressure P2. As a result, the second connection oil passage 42 and the second supply oil passage 32 are in a state in which the hydraulic pressure necessary to maintain the engagement state of the engagement devices C0 and C1 in the steady state is supplied.

  As shown in FIG. 5, in the oil supply device 100 according to the present embodiment, the first hydraulic pump 11 is capable of securing the maximum hydraulic pressure P1 and flow rate Q1 required in the first connection oil passage 41 in a steady state. The second hydraulic pump 12 has a discharge capacity that can ensure the maximum hydraulic pressure P2 and the flow rate Q2 required in the second connection oil passage 42. It only has to be present (see the area indicated by A2 in FIG. 5).

  On the other hand, in the configuration of the comparative example in which the first hydraulic pump 11 supplies the oil F to both the first supply oil passage 31 and the second supply oil passage 32 as in the related art, the first hydraulic pump 11 includes the first hydraulic pump 11. The hydraulic pressure P2 for controlling the engagement devices C0 and C1, which is the maximum hydraulic pressure required in both the connection oil passage 41 and the second connection oil passage 42, and the first connection oil passage 41 and the second connection oil passage. 42 is required to have a discharge capacity that can secure a total flow rate (Q1 + Q2) of the flow rate Q1 and the flow rate Q2, which is a flow rate required for each of the flow rates (indicated by A1, A2, and A3 in FIG. 5). Area reference). That is, in such a configuration of the comparative example, the first hydraulic pump 11 needs to have an ability to perform work of hydraulic pressure P2 × flow rate (Q1 + Q2) (A1 + A2 + A3 in FIG. 5). Therefore, the first hydraulic pump 11 is easily increased in size, and the driving force loss of the internal combustion engine EN and the rotating electrical machine MG that drives the first hydraulic pump 11 is likely to increase. Therefore, there is a problem that the energy efficiency of the vehicle drive device D is deteriorated particularly in a steady state where a large hydraulic pressure is not required.

  In contrast, in the oil supply device 100 according to the present embodiment, as described above, the first hydraulic pump 11 is relatively large in order to supply the lubricating oil F to the lubrication target L in the steady state. Although the flow rate Q1 is required, regarding the hydraulic pressure, it is only necessary to have a discharge capacity capable of ensuring a lubricating hydraulic pressure P1 that is significantly lower than the hydraulic pressure P2 for controlling the engagement devices C0 and C1. That is, in the configuration of the present embodiment, it is sufficient for the first hydraulic pump 11 to be capable of performing work of hydraulic pressure P1 × flow rate Q1 (region A1 in FIG. 5). Therefore, the enlargement of the first hydraulic pump 11 can be suppressed, and the loss of driving force of the internal combustion engine EN and the rotating electrical machine MG that drives the first hydraulic pump 11 can be suppressed to a small value.

  As described above, the second hydraulic pump 12 requires a relatively high hydraulic pressure P2 for controlling the engagement devices C0 and C1, but the flow rate is higher than the lubrication flow rate Q1 for the lubrication target L. What is necessary is just to have the discharge capability which can ensure the flow volume Q2 for control of significantly small engagement apparatus C0 and C1. That is, in the configuration of the present embodiment, it is sufficient that the second hydraulic pump 12 is capable of performing work of the hydraulic pressure P2 × flow rate Q2 (region A2 in FIG. 5). Therefore, the increase in size of the second hydraulic pump 12 can be suppressed, the increase in the size of the electric motor 121 that drives the second hydraulic pump 12 can be suppressed, and the energy efficiency of the second hydraulic pump 12 can be increased. .

  In the overall configuration of the hydraulic pump of the oil supply apparatus 100, in the configuration of the comparative example, the first hydraulic pump 11 performs work corresponding to the area A1 + A2 + A3 in FIG. 5, and as a result, work corresponding to the area A3 in FIG. 5 is wasted. It was. On the other hand, in the configuration of this embodiment, even if both the first hydraulic pump 11 and the second hydraulic pump 12 are combined, only the work corresponding to the area of A1 + A2 in FIG. 5 is performed. The energy for driving can be significantly reduced. Therefore, the energy efficiency of the vehicle drive device D can be greatly improved as compared with the configuration of the comparative example.

2. Second Embodiment Hereinafter, an oil supply apparatus 100 according to a second embodiment will be described with reference to the drawings. The oil supply apparatus 100 according to the second embodiment is different from that of the first embodiment in that it includes a third hydraulic pump 13. Below, it demonstrates centering on difference with the said 1st Embodiment. Note that points not particularly described are the same as those in the first embodiment.

  As shown in FIG. 6, the oil supply apparatus 100 according to the present embodiment includes a third hydraulic pump 13 and a fourth connection oil passage 44 in addition to the configuration of the first embodiment. The third hydraulic pump 13 is electrically driven by a second electric motor 131 that is independent of the power transmission path P and is different from the first electric motor 121 that is the electric motor of the second hydraulic pump 12. This is a hydraulic pump of the type. In the present embodiment, the third hydraulic pump 13 is configured to be able to control the discharge pressure of the oil F, like the second hydraulic pump 12. Specifically, the second electric motor 131 is controlled by the control device 10 so that the discharge pressure of the oil F from the third hydraulic pump 13 becomes a target value. Note that the discharge flow rate of the oil F from the third hydraulic pump 13 may be controlled by controlling the second electric motor 131.

  The third hydraulic pump 13 is connected to the strainer 23 via the third suction oil passage 24. Specifically, a third suction oil passage 24 is connected to the suction port of the third hydraulic pump 13. The third suction oil passage 24 merges with the first suction oil passage 21 and the second suction oil passage 22, and the strainer 23 is connected to the downstream side of the joining portion. The third suction oil passage 24 may be connected to the independent strainer 23 without joining the first suction oil passage 21 and the second suction oil passage 22.

  The fourth connection oil passage 44 is an oil passage that connects the third hydraulic pump 13 and the first connection oil passage 41. In the present embodiment, the fourth connection oil passage 44 is connected to the first branch portion 41a. A third check valve 53 is provided in the middle of the fourth connection oil passage 44. The third check valve 53 is a valve that regulates the flow of the oil F from the first connection oil passage 41 side to the fourth connection oil passage 44 side.

  The third hydraulic pump 13 can secure a hydraulic pressure equal to or higher than the engaging hydraulic pressure P1U, which is the maximum hydraulic pressure required in the first connecting oil path 41, as the hydraulic pressure of the oil F flowing in the fourth connecting oil path 44. Has discharge capacity. Therefore, the oil F discharged from the third hydraulic pump 13 while the first hydraulic pump 11 is being driven can be supplied to the first connection oil passage 41 via the fourth connection oil passage 44. That is, the first hydraulic pump 11 can be assisted by the third hydraulic pump 13. Therefore, as shown in FIG. 7, when the third hydraulic pump 13 discharges the oil F at the specified flow rate Q3 (see the region indicated by A4 in FIG. 7), the maximum discharge flow rate of the first hydraulic pump 11 is changed to the third flow rate. It can be reduced by the specified flow rate Q3 of the hydraulic pump 13 (see the region indicated by A1 in FIG. 7). In the configuration of the present embodiment, it is sufficient for the first hydraulic pump 11 to be capable of performing the work of hydraulic pressure P1 × flow rate (Q1-Q3) (A1 in FIG. 7). Therefore, compared to the first embodiment, the first hydraulic pump 11 can be reduced in size, and the loss of the driving force of the internal combustion engine EN and the rotating electrical machine MG that drives the first hydraulic pump 11 is further reduced. be able to.

3. Other Embodiments (1) In the above embodiment, the configuration in which the second check valve 52 is provided on the upstream side of the second branch portion 42a in the second connection oil passage 42 has been described as an example. However, the second check valve 52 may not be provided without being limited to such a configuration. Further, instead of the second check valve 52, a relief valve may be provided on the upstream side of the second branch portion 42a in the second connection oil passage 42.

(2) In the above embodiment, the configuration in which the second hydraulic pump 12 can control the discharge pressure or the discharge flow rate of the oil F by controlling the rotation speed and torque of the electric motor 121 has been described as an example. However, without being limited to such a configuration, the second hydraulic pump 12 may be basically configured to be driven at a constant rotational speed or a constant torque.

(3) In the above embodiment, the configuration in which the second hydraulic pump 12 reduces the discharge pressure during the engagement operation of the engagement devices C0 and C1 has been described as an example. However, the configuration is not limited to such a configuration, and the second hydraulic pump 12 may be configured to maintain a constant discharge pressure even during the engagement operation of the engagement devices C0 and C1.

(4) In the first embodiment, the feedback connecting the discharge port 6 c of the control valve 6 and the first suction oil passage 21 of the first hydraulic pump 11 and the second suction oil passage 22 of the second hydraulic pump 12. The configuration provided with the oil passage 62 has been described as an example. However, the present invention is not limited to such a configuration, and the return oil passage 62 may not be provided. Alternatively, the return oil passage 62 may be connected only to the first suction oil passage 21 of the first hydraulic pump 11.

(5) In the second embodiment, the configuration in which the third check valve 53 is provided in the middle of the fourth connection oil passage 44 has been described as an example. However, the third check valve 53 may not be provided without being limited to such a configuration.

(6) Note that the configurations disclosed in the above-described embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction arises. Regarding other configurations, the embodiments disclosed herein are merely examples in all respects. Accordingly, various modifications can be made as appropriate without departing from the spirit of the present disclosure.

4). Outline of the above embodiment Hereinafter, an outline of the oil supply apparatus (100) described above will be described.

The oil supply device (100)
A drive provided on a first driving force source (EN, MG) for driving the wheel (W) and a power transmission path (P) connecting the first driving force source (EN, MG) and the wheel (W). An oil supply device that supplies oil (F) to a vehicle drive device (D) including a transmission mechanism (T) and engagement devices (C0, C1) provided in the power transmission path (P). (100),
A first hydraulic pump (11) driven by a driving force transmitted through the power transmission path (P);
A second hydraulic pump (12) driven by a second driving force source (121) independent of the power transmission path (P);
A first supply oil passage (31) for supplying lubricating oil (F) to a lubrication target (L) including the drive transmission mechanism (T);
A second supply oil passage (32) for supplying hydraulic pressure for control to the engagement devices (C0, C1);
A first connection oil passage (41) connecting the first hydraulic pump (11) and the first supply oil passage (31);
A second connection oil passage (42) connecting the second hydraulic pump (12) and the second supply oil passage (32);
A third connection oil passage (43) that connects the first connection oil passage (41) and the second connection oil passage (42) and is provided with a first check valve (51) in the middle thereof; ,
The first check valve (51) regulates the flow of oil (F) from the second connection oil passage (42) side to the first connection oil passage (41) side,
A control valve (6) for controlling the hydraulic pressure of the first connection oil passage (41) on the downstream side of the connection portion (41a) with the third connection oil passage (43) in the first connection oil passage (41). )
The control valve (6) is more than the control valve (6) in the first connection oil passage (41) during the engagement operation for changing the engagement device (C0, C1) from the released state to the engaged state. Engagement operation control is performed in which the upstream hydraulic pressure is higher than the hydraulic pressure of the second connection oil passage (42).

In general, the lubricating oil (F) supplied to the object to be lubricated (L) requires a relatively large flow rate, but the hydraulic pressure may be low. On the other hand, the control hydraulic pressure supplied to the engagement devices (C0, C1) requires a relatively high hydraulic pressure, but the flow rate may be small. According to this configuration, in the steady state other than during the engagement operation of the engagement devices (C0, C1), the first hydraulic pump (11) is lubricated with oil (F) for lubrication (L). The second hydraulic pump (12) supplies the control hydraulic pressure to the engagement devices (C0, C1). Therefore, the first hydraulic pump (11) supplies both the lubricating oil (F) supplied to the lubrication target (L) and the control hydraulic pressure supplied to the engagement devices (C0, C1). In comparison, the maximum value of the discharge hydraulic pressure required for the first hydraulic pump (11) can be kept low. Therefore, the enlargement of the first hydraulic pump (11) can be suppressed, and the loss of the driving force of the vehicle drive device (D) due to the driving of the first hydraulic pump (11) can be suppressed small. .
In the steady state as described above, since the flow rate of the oil (F) supplied for controlling the engagement devices (C0, C1) is small, the discharge flow rate required for the second hydraulic pump (12) is also kept small. be able to. And according to this structure, during the engagement operation | movement which changes an engagement apparatus (C0, C1) from a releasing state to an engagement state, by controlling a control valve (6), a 3rd connection oil path (43 ), The control hydraulic pressure is supplied from the first hydraulic pump (11) to the engagement devices (C0, C1). Therefore, the second hydraulic pump (12) does not need to supply the hydraulic pressure necessary for the engagement operation of the engagement devices (C0, C1), and the engagement state of the engagement devices (C0, C1) in the steady state. Any hydraulic pressure may be supplied as long as it can be supplied. Therefore, the maximum value of the discharge hydraulic pressure required for the second hydraulic pump (12) can be kept low. Therefore, the enlargement of the second hydraulic pump (12) can be suppressed.

  Here, during the engagement operation, the control valve (6) has a hydraulic pressure downstream of the connection portion (42a) with the third connection oil passage (43) in the second connection oil passage (42). It is preferable that the control during the engaging operation is executed so that the hydraulic pressure required for the engaging operation of the engaging devices (C0, C1) is equal to or higher than that.

  According to this configuration, the hydraulic pressure necessary to control the engagement operation of the engagement devices (C0, C1) can be supplied to the second supply oil passage (32), so that the engagement devices (C0, C1) ) Can be appropriately performed.

  In addition, the control valve (6) requires the flow rate of the oil (F) in the first supply oil passage (31) in a steady state other than during the engagement operation during execution of the control during the engagement operation. It is preferable to make it lower than the flow rate.

  According to this configuration, both the hydraulic pressure for controlling the engagement devices (C0, C1) and the lubricating oil (F) for the lubrication target (L) are supplied during execution of the control during the engagement operation. The maximum discharge flow rate of the first hydraulic pump (11) can be kept relatively small. Therefore, the enlargement of the first hydraulic pump (11) can be suppressed, and the loss of driving force due to driving the first hydraulic pump (11) can be further reduced. Even if the flow rate of the lubricating oil (F) supplied to the lubrication target (L) is lower than the required flow rate in the steady state, the lubrication oil (F) exists in various places on the lubrication target (L). Therefore, a problem due to a temporary decrease in the flow rate during the engaging operation hardly occurs.

In addition, a second check valve (52) is provided on the upstream side of the connection portion (42a) with the third connection oil passage (43) in the second connection oil passage (42),
The second check valve (52) is an oil from the connection portion (42a) to the third connection oil passage (43) in the second connection oil passage (42) to the second hydraulic pump (12). It is preferable to regulate the flow of (F).

  According to this configuration, it is possible to prevent the backflow of the oil (F) to the second hydraulic pump (12) during the execution of the engaging operation control. Therefore, it is possible to suppress an excessive load from acting on the second hydraulic pump (12).

  The second hydraulic pump (12) is preferably configured to be able to control the discharge pressure of the oil (F).

  According to this configuration, the second hydraulic pump (12) is controlled according to the state of the engagement devices (C0, C1), and the hydraulic pressure required for the second supply oil passage (32) is appropriately supplied. Can do. Therefore, the necessity of providing the hydraulic control valve (6) in the second connection oil passage (42) connecting the second hydraulic pump (12) and the second supply oil passage (32) can be reduced.

In the configuration in which the second hydraulic pump (12) can control the oil discharge pressure,
It is preferable that the second hydraulic pump (12) lowers the discharge pressure during the engaging operation.

According to this configuration, the difference between the hydraulic pressure of the first connection oil passage (41) and the hydraulic pressure of the second connection oil passage (42) can be increased during the engaging operation. Therefore, the oil (F) can be smoothly supplied from the first hydraulic pump (11) to the second supply oil passage (32).
Further, since the hydraulic pressure is not supplied from the second hydraulic pump (12) to the engaging devices (C0, C1) during the engaging operation, the discharge pressure of the second hydraulic pump (12) is reduced to reduce the first hydraulic pump (12). Loss of energy caused by driving the two hydraulic pumps (12) can be reduced. Further, the load acting on the second hydraulic pump (12) can be reduced.

  Further, it is preferable that the second connection oil passage (42) is not provided with a hydraulic control valve (6) for controlling the oil pressure of the second connection oil passage (42).

  According to this configuration, the configuration of the oil supply device (100) can be simplified.

  The third hydraulic pump (13) is driven by a third driving force source (131) that is independent of the power transmission path (P) and is different from the second driving force source (121). ) And a fourth connection oil passage (44) for connecting the third hydraulic pump (13) and the first connection oil passage (41).

  Generally, the required flow rate of the lubricating oil (F) supplied to the lubrication target (L) varies depending on the operating state of the vehicle drive device (D), and the maximum flow rate is required because of the high speed of the vehicle It is often only a relatively limited operating state such as during travel. According to this configuration, the lubricating oil (F) can be supplied to the lubrication target (L) not only by the first hydraulic pump (11) but also by the third hydraulic pump (13). Therefore, when the required flow rate of the lubricating oil (F) supplied to the lubrication target (L) is relatively large, both the first hydraulic pump (11) and the third hydraulic pump (13) are used, and the lubricating oil is used. By not using the third hydraulic pump (13) in a steady state where the required flow rate of (F) is relatively small, the maximum discharge flow rate of the first hydraulic pump (11) can be kept small. Therefore, the loss of driving force due to driving the first hydraulic pump (11) can be further reduced.

  Further, the suction oil passage (21) connected to the suction port of the first hydraulic pump (11) further includes a return oil passage (62) for connecting the discharge port (6c) of the control valve (6). It is preferable that

  According to this configuration, as a result of the hydraulic pressure being adjusted by the control valve (6), the oil (F) discharged from the control valve (6) is returned to the suction oil passage (21) through the return oil passage (62). Can do. Therefore, the amount of oil (F) returned to the suction port of the first hydraulic pump (11) is increased, and the oil (F) sucked from the oil reservoir (S) by the first hydraulic pump (11) through the strainer (23). ) Can be reduced. Therefore, the first hydraulic pump (11) can be prevented from sucking air, and the efficiency of the first hydraulic pump (11) can be increased.

  The technology according to the present disclosure includes a first driving force source that drives a wheel, a drive transmission mechanism that is provided in a power transmission path that connects the first driving force source and the wheel, and a power transmission path that is provided in the power transmission path. It can utilize for the oil supply apparatus which supplies oil to the vehicle drive device provided with the engagement apparatus.

DESCRIPTION OF SYMBOLS 100: Oil supply apparatus 11: 1st hydraulic pump 12: 2nd hydraulic pump 121: Electric motor 31: 1st supply oil path 32: 2nd supply oil path 41: 1st connection oil path 42: 2nd connection oil path 43 : Third connecting oil passage 51: first check valve 52: second check valve 6: control valve 10: control device F: oil D: vehicle drive device W: wheel EN: internal combustion engine (first drive force source) )
MG: Rotating electric machine (first driving force source)
C0: Starting engagement device (engagement device)
C1: Shift engagement device (engagement device)
P: Power transmission path T: Drive transmission mechanism L: Lubrication target

Claims (9)

A first driving force source for driving a wheel; a drive transmission mechanism provided in a power transmission path connecting the first driving force source and the wheel; and an engagement device provided in the power transmission path. An oil supply device for supplying oil to a vehicle drive device,
A first hydraulic pump driven by a driving force transmitted through the power transmission path;
A second hydraulic pump driven by a second driving force source independent of the power transmission path;
A first supply oil passage for supplying lubricating oil to a lubrication target including the drive transmission mechanism;
A second supply oil path for supplying control hydraulic pressure to the engagement device;
A first connection oil passage connecting the first hydraulic pump and the first supply oil passage;
A second connection oil passage connecting the second hydraulic pump and the second supply oil passage;
Connecting the first connection oil passage and the second connection oil passage, and a third connection oil passage provided with a first check valve in the middle,
The first check valve regulates the flow of oil from the second connection oil passage side to the first connection oil passage side,
A control valve for controlling the hydraulic pressure of the first connection oil passage is provided on the downstream side of the connection portion with the third connection oil passage in the first connection oil passage,
During the engagement operation for changing the engagement device from the disengaged state to the engaged state, the control valve applies a hydraulic pressure upstream of the control valve in the first connection oil passage to a hydraulic pressure in the second connection oil passage. An oil supply apparatus that performs control during engagement operation to be higher than the above.   The control valve is configured such that, during the engagement operation, the hydraulic pressure downstream of the connection portion with the third connection oil passage in the second connection oil passage is equal to or higher than the oil pressure necessary for the engagement operation of the engagement device. The oil supply apparatus according to claim 1, wherein the control during the engagement operation is executed so that   The control valve makes the flow rate of oil in the first supply oil passage lower than a required flow rate in a steady state other than during the engagement operation during execution of the control during the engagement operation. The oil supply apparatus described in 1. A second check valve is provided on the upstream side of the connection portion with the third connection oil passage in the second connection oil passage,
The said 2nd non-return valve regulates the flow of the oil from the said connection part with the said 3rd connection oil path in the said 2nd connection oil path to the said 2nd hydraulic pump. The oil supply apparatus according to item.   The oil supply device according to any one of claims 1 to 4, wherein the second hydraulic pump is configured to be capable of controlling an oil discharge pressure.   The oil supply device according to claim 5, wherein the second hydraulic pump reduces the discharge pressure during the engaging operation.   The oil supply apparatus according to any one of claims 1 to 6, wherein a hydraulic control valve that controls a hydraulic pressure of the second connection oil passage is not provided in the second connection oil passage. A third hydraulic pump that is independent of the power transmission path and is driven by a third driving force source that is a driving force source different from the second driving force source;
A fourth connection oil passage connecting the third hydraulic pump and the first connection oil passage;
The oil supply device according to any one of claims 1 to 7, further comprising:   The oil supply apparatus according to any one of claims 1 to 8, further comprising a return oil path that connects a discharge port of the control valve to an intake oil path connected to the suction port of the first hydraulic pump. .

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