JP2010164177A - Power transmitting device and vehicle having power transmitting device mounted thereon - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the size in a device relating to a power transmitting device and a vehicle having the power transmitting device mounted thereon. <P>SOLUTION: A path of an operating oil for lubricating a lubrication subject of an automatic transmission is divided into two paths: a lubricating oil path 58b to be mainly used for a clutch or a brake as a lubrication subject, and a lubrication oil path 79 to be mainly used for a gear mechanism such as a differential gear. Through the lubricating oil path 58b, the operating oil is supplied by a mechanical oil pump 42. Through the lubricating oil path 79, the operating oil is supplied by an electromagnetic pump 100. The electromagnetic pump 100 supplies the operating oil to an oil path 48 of the clutch C1 or supplies the operating oil to the lubricating oil path 79 and a fluid coupling 21 by means of a switching valve 70. This configuration can reduce a load on a mechanical oil pump 42 when an engine rotational speed Ne is low, so that the entire device can be reduced in size. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a power transmission device that is mounted on a vehicle and includes a clutch that transmits power from a prime mover to an axle side, and a vehicle on which the power transmission device is mounted.

  Conventionally, as this kind of power transmission device, there are a first hydraulic pump (mechanical oil pump) driven by power from an engine, a manual shift valve interlocked with a shift operation, and a manual shift valve in the first hydraulic pump. The oil passage is blocked from the first position that is connected to the oil passage that is connected to the solenoid valve to which the input port is connected via the oil passage, and the oil passage that connects the output port of the solenoid valve and the friction engagement device (clutch). A selection valve configured as a two-position electromagnetic valve that selects a second position (including a built-in check valve), a second hydraulic pump (electromagnetic pump) that directly supplies discharge pressure to the clutch, Have been proposed (see, for example, Patent Document 1). In this device, pressure oil is supplied from the first hydraulic pump through the selection valve when the friction engagement device that requires high pressure and large capacity is operated, and pressure oil is supplied from the second hydraulic pump when the friction engagement device is held. By doing so, energy loss can be reduced and energy can be saved.

JP 2008-180303 A

  By the way, hydraulic oil discharged from a mechanical oil pump is generally used for lubrication of clutches, bearings, gears, and the like included in a power transmission device. The engine is designed in consideration of the idling rotation speed, the hydraulic pressure required for engaging the clutch, and the hydraulic pressure required for supplying hydraulic oil to the lubrication part. On the other hand, considering that the power transmission device is mounted on the vehicle, the mounting space is limited, so using a mechanical oil pump with a capacity as low as possible reduces the size of the mechanical oil pump, and thus the device. This can be considered as an important issue in reducing the overall size.

  The power transmission device of the present invention and a vehicle equipped with the power transmission device are mainly intended to reduce the size of a pump that is operated by power from a prime mover while exhibiting the performance of the device.

  The power transmission device of the present invention and a vehicle equipped with the power transmission device employ the following means in order to achieve the main object described above.

The power transmission device of the present invention is
A power transmission device including a clutch mounted on a vehicle and transmitting power from a prime mover to an axle,
A first pump that is driven by power from the prime mover to generate and output a fluid pressure;
A second pump that is driven by power supply to generate and output a fluid pressure;
A pressure regulating valve that regulates the working fluid output from the first pump and supplies at least a part of the working fluid discharged along with the regulation to the first lubrication target for lubrication;
When the first pump is driven, the working fluid output from the pressure regulating valve is supplied to the clutch, and the working fluid output from the second pump is used for lubrication as the first lubrication target. A first connection state in which the supply of working fluid from the second pump to the clutch is cut off, and the pressure adjustment when the first pump is not driven. The supply of the working fluid from the valve to the clutch is shut off, and the working fluid output from the second pump is supplied to the clutch, and the working fluid is supplied from the second pump to the second lubrication target. A switching valve for switching between a second connection state in which is cut off,
It is a summary to provide.

  In this power transmission device of the present invention, the pressure regulating valve regulates the working fluid output from the first pump driven by the power from the prime mover and at least part of the working fluid discharged along with the pressure regulation. Supplyed to the first lubrication object for lubrication, when the first pump is driven by the switching valve, the working fluid output from the pressure regulating valve is supplied to the clutch and output from the second pump A first connection state in which the working fluid is supplied to a second lubrication object different from the first lubrication object for lubrication, and the supply of the working fluid from the second pump to the clutch is interrupted; When not driven, the supply of the working fluid from the pressure regulating valve to the clutch is shut off, and the working fluid output from the second pump is supplied to the clutch and is supplied from the second pump to the second lubrication target. Switching a second connection state in which the supply of the dynamic fluid is blocked. By supplying the working fluid to the second lubrication target by the second pump driven by the supply of electric power, it is only necessary to supply the working fluid from the first pump only to the first lubrication target. As compared with a pump that supplies a working fluid from one pump to both the first lubrication object and the second lubrication object, a low-capacity pump can be used as the first pump. As a result, the entire apparatus can be further downsized. Further, if the second pump is driven while the first pump is stopped along with the stoppage of the prime mover, the switching valve is fluid pressure from the second pump to the clutch in the second connection state. Therefore, when the prime mover is started and the switching valve is in the first connection state, the clutch can be quickly engaged, and power transmission can be started quickly. Here, the “motor” includes an internal combustion engine capable of automatic stop and automatic start, and also includes an electric motor. The “clutch” includes a normal clutch that connects two rotating systems, and also includes a brake that connects one rotating system to a stationary system such as a case. Furthermore, the "second pump" includes a normal electric pump that generates fluid pressure by being driven by power from an electric motor, and fluid pressure that is generated by reciprocating a movable portion by electromagnetic force and spring biasing force. Includes electromagnetic pumps to be generated.

  Such a power transmission device of the present invention includes a fluid transmission device that transmits power by the working fluid in the working fluid chamber with the inflow and outflow of the working fluid in the working fluid chamber, and the second pump includes the switching When the valve is in the first state, the working fluid may be supplied to the second lubrication target through the working fluid chamber. In this case, the fluid transmission device can be operated using the working fluid output from the second pump, so that the first pump can be reduced in capacity and the first pump can be further downsized. can do.

  In the power transmission device according to the present invention, the switching valve may include a signal pressure input port for inputting the working fluid output from the first pump and a first input of the working fluid output from the pressure regulating valve. An input port, a second input port for inputting the working fluid output from the second pump, a first output port for outputting the working fluid to the clutch, and a working fluid for the second lubrication target And when the fluid pressure is acting on the signal pressure input port, the first input port and the first output port are connected as the first connection state. And disconnecting the connection between the second input port and the first output port and connecting the second input port and the second output port so that fluid pressure acts on the signal pressure input port. Tena Sometimes, as the second connection state, the connection between the first input port and the first output port is cut off, and the second input port and the first output port are connected and the second input is connected. It may be formed so as to cut off the connection between the port and the second output port. In this way, since the connection state can be switched with only one switching valve, the apparatus can be further downsized as compared with the connection state switching using two or more switching valves. .

The vehicle of the present invention
Prime mover,
The power transmission device of the present invention according to any one of the aspects described above, that is, a power transmission device that basically includes a clutch that is mounted on a vehicle and transmits power from the prime mover to the axle. A first pump that is driven by power to generate and output a fluid pressure, a second pump that is driven by power supply to generate and output a fluid pressure, and is output from the first pump. A pressure regulating valve for regulating the pressure of the working fluid and supplying at least a part of the working fluid discharged with the pressure regulation to the first lubrication object for lubrication, and when the first pump is driven The working fluid output from the pressure regulating valve is supplied to the clutch, and the working fluid output from the second pump is supplied to a second lubrication target different from the first lubrication target for lubrication. Said The first connection state in which the supply of the working fluid from the pump to the clutch is cut off, and the supply of the working fluid from the pressure regulating valve to the clutch is cut off when the first pump is not driven A switching valve that switches between a second connection state in which the working fluid output from the second pump is supplied to the clutch and the supply of the working fluid from the second pump to the second lubrication target is shut off. And a power transmission device comprising:

  According to the vehicle of the present invention, since the power transmission device of the present invention according to any one of the aspects described above is mounted, the effect exerted by the power transmission device of the present invention, for example, the entire device can be further reduced in size. An effect, the effect that a clutch can be quickly engaged at the time of restart after a stop of a prime mover, and power transmission can be started quickly can be achieved.

It is a block diagram which shows the outline of a structure of the motor vehicle 10 in which the power transmission device 20 as one Example of this invention was integrated. 1 is a configuration diagram showing an outline of a configuration of an automatic transmission 30 provided in a power transmission device 20. FIG. 3 is an explanatory diagram showing an operation table of the automatic transmission 30. FIG. FIG. 2 is a configuration diagram showing an outline of a configuration of a hydraulic circuit 40. It is explanatory drawing which shows the relationship between the engine rotational speed Ne and the discharge flow rate Q of the mechanical oil pump.

  Next, embodiments of the present invention will be described using examples.

  FIG. 1 is a configuration diagram showing an outline of the configuration of an automobile 10 incorporating a power transmission device 20 as an embodiment of the present invention, and FIG. 2 shows an outline of the configuration of an automatic transmission 30 provided in the power transmission device 20. FIG. 3 is an explanatory diagram showing an operation table of the automatic transmission 30, and FIG. 4 is a schematic diagram showing a schematic configuration of a hydraulic circuit 40 that drives the automatic transmission 30.

  As shown in FIG. 1, an automobile 10 according to an embodiment includes an engine 12 as an internal combustion engine that outputs power by explosion combustion of a hydrocarbon-based fuel such as gasoline or light oil, and an electronic control for the engine that controls the operation of the engine 12. Connected to a drive shaft 94 connected to a unit (engine ECU) 16 and the crankshaft 14 of the engine 12 and to the left and right wheels 90a, 90b via a differential gear 92 to drive power from the engine 12 to the drive shaft 94, and the power transmission device 20 of the embodiment that transmits to 94.

  As shown in FIG. 1, the power transmission device 20 of the embodiment is configured as a transaxle device that transmits power from the engine 12 to the drive shaft 94, and is connected to the crankshaft 14 of the engine 12. A fluid coupling (fluid coupling) 21 with a lock-up clutch as a fluid transmission device comprising a pump impeller 23 and an output-side turbine runner 24, and hydraulic oil is disposed by the power from the engine 12 that is disposed downstream of the fluid coupling 21. A mechanical oil pump 42 for pumping, an input shaft 36 connected to the turbine runner 24 of the fluid coupling 21, and an output shaft 38 connected to the drive shaft 94 are used to shift the power input to the input shaft 36. A hydraulically driven stepped automatic transmission 30 that outputs to the output shaft 38, and this automatic transmission It includes a hydraulic circuit 40 as an actuator for driving the down 30, an electronic control unit (ATECU) 26 for automatic transmission that controls the automatic transmission 30 (hydraulic circuit 40), and a main electronic control unit 80 that controls the entire vehicle. The main electronic control unit 80 includes a shift position SP from the shift position sensor 82 that detects the operation position of the shift lever 81 and an accelerator opening Acc from the accelerator pedal position sensor 84 that detects the amount of depression of the accelerator pedal 83. A brake switch signal BSW from the brake switch 86 that detects depression of the brake pedal 85, a vehicle speed V from the vehicle speed sensor 88, and the like are input. The main electronic control unit 80 is connected to the engine ECU 16 and the ATECU 26 via a communication port, and exchanges various control signals and data with the engine ECU 16 and the ATECU 26.

  As shown in FIG. 1 or FIG. 4, the fluid coupling 21 is connected to a pump impeller 23 connected to the crankshaft 14 of the engine 12 via a coupling cover 22 and to an input shaft 36 of the automatic transmission 30. And a turbine runner 24 arranged opposite to each other, and using the hydraulic oil in the coupling chamber 21a formed by the coupling cover 22, the pump impeller 23 converts the engine torque into the flow of hydraulic oil and The turbine runner 24 converts the flow into torque on the input shaft 36 of the automatic transmission 30 to transmit torque. The fluid coupling 30 incorporates a multi-plate lockup clutch 25 that locks up the pump impeller 23 and the turbine runner 24. The multi-plate lockup clutch 25 includes a clutch piston 25a that forms a lockup chamber 21b partitioned with respect to the coupling chamber 21a, and a first friction material affixed to the surface of the clutch piston 25a by spline fitting. 1 clutch plate and a plurality of clutch plates 25b which are spline-fitted to the coupling cover 22 and a second clutch plate having a friction material attached to the surface thereof. The clutch plate 25b is engaged and locked up by the differential pressure between the oil pressure and the oil pressure in the lockup chamber 21b, or the clutch plate 25b is released and the lockup is released. Further, the fluid coupling 21 has an introduction port 22a for introducing hydraulic oil into the coupling chamber 21a, a discharge port 22b for discharging hydraulic oil in the coupling chamber 21a, and a lockup chamber 21b. Thus, an input / output port 22c for inputting / outputting hydraulic oil is formed.

  As shown in FIG. 2, the automatic transmission 30 includes a double-pinion planetary gear mechanism 30a, two single-pinion planetary gear mechanisms 30b and 30c, three clutches C1, C2, and C3, and four brakes B1, B2, and so on. B3, B4 and three one-way clutches F1, F2, F3 are provided. The double pinion type planetary gear mechanism 30a includes a sun gear 31a as an external gear, a ring gear 32a as an internal gear arranged concentrically with the sun gear 31a, and a plurality of first pinion gears 33a meshing with the sun gear 31a. A carrier 35a that engages with the first pinion gear 33a and meshes with the ring gear 32a and connects the plurality of first pinion gears 33a and the plurality of second pinion gears 34a so as to rotate and revolve freely. The sun gear 31a is connected to the input shaft 36 via the clutch C3, and the rotation of the brake B3 connected via the one-way clutch F2 can be restricted freely or in one direction. The ring gear 32a is turned on and off by the brake B2. It has become the rotation to freely or fixed, the carrier 35a is adapted to the rotation by release of the brake B1 while being restricted its rotation in one direction by the one-way clutch F1 freely or fixed. The single-pinion type planetary gear mechanism 30b includes a sun gear 31b as an external gear, a ring gear 32b as an internal gear disposed concentrically with the sun gear 31b, and a plurality of pinion gears that mesh with the sun gear 31b and mesh with the ring gear 32b. 33b and a carrier 35b that holds the plurality of pinion gears 33b so as to rotate and revolve freely. The sun gear 31b is connected to the input shaft 36 via the clutch C1, and the ring gear 32b is a double-pinion planetary gear mechanism 30a. The carrier 35b is connected to the input shaft 36 via the clutch C2 and can be rotated by the one-way clutch F3. Can be regulated in the direction . The single-pinion planetary gear mechanism 30c includes a sun gear 31c as an external gear, a ring gear 32c as an internal gear arranged concentrically with the sun gear 31c, and a plurality of gears meshed with the sun gear 31c and meshed with the ring gear 32c. The pinion gear 33c and a carrier 35c that holds the plurality of pinion gears 33c so as to rotate and revolve freely. The sun gear 31c is connected to the sun gear 31b of the single pinion planetary gear mechanism 30b, and the ring gear 32c is a single pinion type. It is connected to the carrier 35b of the planetary gear mechanism 30b, and its rotation can be freely or fixed by turning on and off the brake B4. The carrier 35c is connected to the output shaft 38.

  As shown in FIG. 3, the automatic transmission 30 can be switched between forward 1st to 5th, reverse, and neutral by turning on and off the clutches C1 to C3 and turning on and off the brakes B1 to B4. The state of the first forward speed, that is, the state in which the rotation of the input shaft 36 is decelerated at the largest reduction ratio and transmitted to the output shaft 38 is when the clutch C1 is turned on and the clutches C2 and C3 and the brakes B1 to B4 are turned off. Can be formed. In this forward first speed state, the brake B4 is turned on instead of the one-way clutch F3 during engine braking. The second forward speed state can be formed by turning on the clutch C1 and the brake B3 and turning off the clutches C2, C3 and the brakes B1, B2, B4. In the second forward speed state, the brake B2 is turned on instead of the one-way clutch F1 and the one-way clutch F2 during engine braking. The state of the third forward speed can be formed by turning on the clutches C1, C3 and the brake B3 and turning off the clutch C2 and the brakes B1, B2, B4. In the third forward speed state, the brake B1 is turned on instead of the one-way clutch F1 during engine braking. The state of the fourth forward speed can be formed by turning on the clutches C1 to C3 and the brake B3 and turning off the brakes B1, B2, and B4. The state of the fifth forward speed, that is, the state where the rotation of the input shaft 36 is decelerated (accelerated) with the smallest reduction ratio and transmitted to the output shaft 38, the clutches C2 and C3 and the brakes B1 and B3 are turned on and the clutch It can be formed by turning off C1 and brakes B2 and B4. Further, in the automatic transmission 30, the neutral state, that is, the separation of the input shaft 36 and the output shaft 38 can be performed by turning off all the clutches C1 to C3 and the brakes B1 to B4. The reverse state can be formed by turning on the clutch C3 and the brake B4 and turning off the clutches C1 and C2 and the brakes B1 to B3.

  The hydraulic circuit 40 turns on and off the clutches C1 to C3 and the brakes B1 to B4 in the automatic transmission 30. As shown in FIG. 4, the hydraulic circuit 40 regulates hydraulic oil pumped through a strainer 41 from a mechanical oil pump 42 driven by power from the engine 12 to generate a line pressure PL and a line pressure PL. The regulator valve 50 for supplying at least a part of the hydraulic oil to the oil passage 58a with the generation of the pressure, and the modulator pressure PMOD generated via the modulator valve (not shown) from the line pressure PL is adjusted and output as a signal pressure. The linear solenoid SLT that drives the regulator valve 50, the cooler CO that cools the hydraulic oil supplied from the regulator valve 50 to the oil passage 58a and outputs it to the lubricating oil passage (LUBE) 58b, and the oil supplied to the oil passage 58a. A bypass valve 59 for supplying hydraulic oil to the lubricating oil passage 58b by bypassing the cooler CO; An input port 45a for inputting a pressure PL, an output port 45b for D (drive) position, an output port 45c for R (reverse) position, etc. are formed, and a manual valve 45 that opens and closes each port in conjunction with the operation of the shift lever 81. A linear solenoid SLC1 that inputs hydraulic oil output from the D-position output port 45b of the manual valve 45 through the input port 112, adjusts the pressure with discharge to the drain port 116, and outputs the pressure from the output port 114; The electromagnetic pump 100 that sucks hydraulic oil from the oil passage 46 between the strainer 41 and the mechanical oil pump 42 via the suction port 102 and discharges it from the discharge port 104, and the hydraulic oil output from the linear solenoid SLC1 are clutched. C1 oil passage 48 and electromagnetic pump 100 The state in which the hydraulic oil from the discharge port 104 is supplied to the fluid coupling 21 and the supply of hydraulic oil from the linear solenoid SLC1 to the oil passage 48 of the clutch C1 are shut off, and the hydraulic oil from the discharge port 104 is supplied to the oil passage 48 of the clutch C1. A switching valve 60 for switching between the state of supplying the fluid and the modulator valve 70 for reducing the pressure of the hydraulic oil supplied from the electromagnetic pump 100 via the switching valve 60 and supplying it to the coupling chamber 21a (introduction port 22a) of the fluid coupling 21. Then, the line pressure PL is input via the input port 122, and the pressure is adjusted with discharge to the drain port 126, and is supplied to the lockup chamber 21 b (input / output port 22 c) of the fluid coupling 21 via the output port 124. It consists of a linear solenoid SLU that locks up and unlocks by Yes. In FIG. 4, the hydraulic systems of the clutches C2 and C3 other than the clutch C1 and the brakes B1 to B4 are omitted because they do not form the core of the present invention. For these hydraulic systems, well-known linear solenoids are used. Can be configured.

  As shown in FIG. 4, the regulator valve 50 is connected to a signal pressure input port 52 a for inputting the output pressure from the linear solenoid SLT as a signal pressure and an oil passage 44 of the output of the mechanical oil pump 42 to feed back the line pressure PL. A sleeve 52 formed with various ports including a feedback input port 52b for inputting pressure, an input port 52c connected to the oil passage 44, an output port 52d connected to the oil passage 58a connected to the cooler C0, and a drain port 52e. And a spool 54 that slides in the sleeve 52 in the axial direction, and a spring 56 that biases the spool 54 in the axial direction. In the primary regulator valve 50, the amount of oil output from the input port 52c via the output port 52d increases as the spool 54 moves downward in the drawing, and when the spool 54 moves further downward, the drain port 52e is moved from the input port 52c. The hydraulic oil from the mechanical oil pump 42 is reduced by draining the hydraulic oil through the hydraulic pressure to adjust the line pressure. The spool 54 is biased upward in the figure by the spring force of the spring 56 and the hydraulic pressure acting on the signal pressure input port 52a, and is biased downward in the figure by the line pressure PL acting on the feedback input port 52b. The higher the oil pressure acting on the signal pressure input port 52a, the higher the line pressure PL.

  As shown in FIG. 4, the switching valve 60 is connected to a signal pressure input port 62a for inputting the line pressure PL as a signal pressure, an input port 62b connected to the output port 114 of the linear solenoid SLC1, and a discharge port 104 of the electromagnetic pump 100. Various types of the input port 62c connected, the output port 62d connected to the oil passage 48 of the clutch C1, and the output port 62e connected to the oil passage 68 connected to the introduction port 22a of the fluid coupling 21 via the modulator valve 70. The sleeve 62 is formed with a port, a spool 64 that slides in the sleeve 62 in the axial direction, and a spring 66 that biases the spool 64 in the axial direction. When the line pressure PL is input to the signal pressure input port 62a, the switching valve 60 overcomes the urging force of the spring 66 and the spool 64 moves to the position shown in the left half region in the figure, and the input port 62c and the output port The communication between the output port 114 of the linear solenoid SLC1 and the oil passage 48 of the clutch C1 is communicated by disconnecting the communication with the input port 62b and connecting the output port 62d with the input port 62c and the output port 62e. The communication between the discharge port 104 of the electromagnetic pump 100 and the oil passage 48 of the clutch C1 is cut off, and the discharge port 104 and the oil passage 68 directed to the fluid coupling 21 are connected, and the line pressure PL is input to the signal pressure input port 62a. When it is not, the spool 64 is shown in the right half of the figure by the biasing force of the spring 66. The position of the input port 62b and the output port 62d is cut off, the input port 62c and the output port 62d are connected, and the communication between the input port 62c and the output port 62e is cut off, thereby outputting the linear solenoid SLC1. The communication between the port 114 and the oil passage 48 of the clutch C1 is cut off, the discharge port 104 of the electromagnetic pump 100 and the oil passage 48 of the clutch C1 are connected, and the communication between the discharge port 104 and the oil passage 68 is cut off.

  The discharge port 22b of the fluid coupling 21 is connected to a lubricating oil passage (LUBE) 79 that is different from the lubricating oil passage 58b, and the line pressure PL is input to the signal pressure input port 62a of the switching valve 60. By driving the electromagnetic pump 100 in a state where the port 62c and the output port 62e are in communication with each other, the hydraulic oil pressure-fed from the electromagnetic pump 100 is changed over to the switching valve 70 (input port 62c and output port 62e), oil path 68, The oil is supplied to the lubricating oil passage 79 through the modulator valve 70 and the fluid coupling 21 (the introduction port 22a and the discharge port 22b) in this order. In the embodiment, the hydraulic oil supplied to the lubricating oil path 58b is mainly the clutch among mechanical parts (for example, the clutches C1 to C3, the brakes B1 to B4, the differential gear 92, the bearings, and the like) that require lubrication of the automatic transmission 30. The hydraulic fluid supplied to C1 to C3 and brakes B1 to B4 and output from the discharge port 22b of the fluid coupling 21 to the oil passage 79 is supplied mainly to a gear mechanism such as a differential gear 92 in the mechanical portion of the automatic transmission 30. The hydraulic circuit 40 was configured as described above.

  In the vehicle 10 of the embodiment configured in this way, when the shift lever 62 is traveling in the “D (drive)” travel position, the vehicle speed V is set to 0, the accelerator is off, the brake switch signal BSW is on, and so on. When all of the set automatic stop conditions are satisfied, the engine 12 is automatically stopped. When the engine 12 is automatically stopped, thereafter, the engine 12 that has been automatically stopped is automatically started when a preset automatic start condition such as the brake switch signal BSW being turned off is satisfied.

  In the automobile 10 of the embodiment, when the automatic stop condition is satisfied and the engine 12 is automatically stopped, the mechanical oil pump 42 is also stopped accordingly, so the line pressure PL is released and the spool 64 of the switching valve 60 is linear. The communication between the output port 114 of the solenoid SLC1 and the oil passage 48 of the clutch C1 is cut off, and the oil passage 48 of the clutch C1 and the discharge port 104 of the electromagnetic pump 100 are connected. Therefore, hydraulic pressure can be applied to the clutch C1 by pumping hydraulic oil from the electromagnetic pump 100. Next, when the engine 12 that has been stopped due to the automatic start condition is automatically started, the mechanical oil pump 42 is actuated accordingly to supply the line pressure PL, and the spool 64 of the switching valve 60. Connects the output port 114 of the linear solenoid SLC1 and the oil passage 48 of the clutch C1, and blocks the communication between the oil passage 48 of the clutch C1 and the discharge port 104 of the electromagnetic pump 100. At this time, the linear solenoid SLC1 regulates the line pressure PL input via the D-position output port 45b of the manual valve 45 and supplies it to the clutch C1, thereby completely engaging the clutch C1 and starting the vehicle. Can be made. In this way, by driving the electromagnetic pump 100 and applying hydraulic pressure to the clutch C1 while the engine 12 is automatically stopped, the clutch C1 is quickly moved by the linear solenoid SLC1 immediately after the engine 12 is automatically started. Since it can be engaged, the start with the automatic start of the engine 12 can be performed smoothly. In the embodiment, the electromagnetic pump 100 sets the pumping amount so that the hydraulic oil can be replenished by an amount leaking from a seal ring or the like provided between the piston of the clutch C1 and the drum.

  Further, in the automobile 10 of the embodiment, when the engine 12 is in operation, the mechanical oil pump 42 is operated by the power from the engine 12, so that the hydraulic oil pumped from the mechanical oil pump 42 is the line pressure PL. The hydraulic oil that is used to engage the clutches C1 to C3 and the brakes B1 to B4 and is discharged along with the generation of the line pressure is supplied from the regulator valve 50 to the lubricating oil path 58b via the cooler CO. On the other hand, when the line pressure PL is input to the signal pressure input port 62a, the spool 64 of the switching valve 60 communicates the discharge port 104 of the electromagnetic pump 100 and the oil passage 68. The hydraulic oil is supplied to the joint 21 to be used for power transmission in the fluid coupling 21, and the hydraulic oil discharged from the fluid coupling 21 is supplied to the lubricating oil passage 79.

  FIG. 5 shows the relationship between the engine speed Ne and the discharge flow rate Q of the mechanical oil pump 42. As described above, the regulator valve 50 regulates the hydraulic oil pumped from the mechanical oil pump 42 to generate the line pressure PL, and at least a part of the hydraulic oil to the oil passage 58a as the line pressure PL is generated. Therefore, when the rotational speed of the engine 12 is low and the hydraulic oil pumped from the mechanical oil pump 42 is small, the hydraulic oil supplied to the lubricating oil passage 58b is also small. For this reason, if the hydraulic oil necessary for lubrication of all the lubrication targets of the automatic transmission 30 is supplied by the mechanical oil pump 42, even if the engine speed Ne is low, the minimum necessary hydraulic fluid for all lubrication targets Since a relatively high discharge capacity is designed (see line A in the figure), the discharge capacity becomes excessive as the engine speed Ne increases. In the embodiment, the path of the hydraulic oil for lubricating the lubrication target of the automatic transmission 30 includes a lubrication oil path 58b mainly lubricating the clutches C1 to C3 and the brakes B1 to B4 and a gear mechanism such as the differential gear 92. The lubricating oil passage 79 is divided into two parts, and the lubricating oil passage 58b is supplied with hydraulic oil by the mechanical oil pump 42, and the lubricating oil passage 79 is supplied with hydraulic oil by the electromagnetic pump 100. The burden on the mechanical oil pump 42 when the engine speed Ne is low can be reduced (see line B in the figure). Therefore, the mechanical oil pump 42 having a relatively low capacity can be used, and the mechanical oil pump 42 can be downsized. In the embodiment, the mechanical oil pump 42 is connected to each solenoid (linear solenoid SLC1, linear solenoid SLT, etc.), various valves, fluid coupling 21 and the like provided in the hydraulic circuit 40 other than the lubricating oil passage 79 while the engine 12 is idling. The capacity was designed so that the minimum required amount of hydraulic fluid was taken into account.

  According to the power transmission device 20 of the above-described embodiment, the hydraulic oil path 58b mainly for the clutches C1 to C3 and the brakes B1 to B4 is used as a lubricating oil path for lubricating the lubrication target of the automatic transmission 30. The gear mechanism such as the differential gear 92 is mainly divided into two lubrication oil passages 79 to be lubricated. The lubricating oil passage 58b is supplied with hydraulic oil by the mechanical oil pump 42, and the lubricating oil passage 79 is electromagnetically pumped. Since hydraulic oil is supplied by 100, the burden on the mechanical oil pump 42 when the engine speed Ne is low can be reduced, and the mechanical oil pump 42 can be made smaller by using a low-capacity one. be able to. As a result, the entire apparatus can be further downsized. In addition, by reducing the size of the mechanical oil pump 42, the engine 12 can be operated efficiently, so that the fuel consumption can be further improved. Moreover, the discharge port 104 of the electromagnetic pump 100 is connected to the oil passage 48 and the lubricating oil passage 79 of the clutch C1 via the switching valve 70, and the electromagnetic pump 100 is driven while the engine 12 is automatically stopped. Thus, the hydraulic pressure from the electromagnetic pump 100 is applied to the starting clutch C1 via the switching valve 70 instead of the linear solenoid SLC1, so that the clutch C1 is released by the linear solenoid SLC1 immediately after the engine 12 is automatically started. It is possible to engage quickly, and start with the automatic start of the engine 12 can be performed smoothly. Further, the switching valve 60 is used to supply hydraulic oil to the clutch C1 while the engine 12 is automatically stopped and supply hydraulic oil to the lubricating oil passage 79 while the engine 12 is operating. Therefore, the entire apparatus can be reduced in size as compared with the one using two electromagnetic pumps. Further, since the lubricating oil passage 79 is connected to the discharge port 104 of the electromagnetic pump 100 via the switching valve 60 and the fluid coupling 21, the fluid coupling 21 can also be operated using the hydraulic oil pumped from the electromagnetic pump 100. it can. As a result, the load on the mechanical oil pump 42 can be further reduced as compared with the case where the hydraulic oil pumped from the mechanical oil pump 42 is supplied to the fluid coupling 21, and the mechanical oil pump 42 is further downsized. can do.

  In the power transmission device 20 of the embodiment, among the lubrication targets of the automatic transmission 30, hydraulic oil is supplied by the mechanical oil pump 42 for the lubrication oil path 58 b mainly for the clutches C1 to C3 and the brakes B1 to B4. The lubricating oil passage 79 that mainly lubricates a gear mechanism such as the differential gear 92 is supplied with hydraulic oil by the electromagnetic pump 100, but is not limited thereto, and the operation from the mechanical oil pump 42 is not limited thereto. The lubrication target to be lubricated with oil and the lubrication target to be lubricated with the hydraulic oil from the electromagnetic pump 100 may be separated in any way.

  In the power transmission device 20 of the embodiment, the hydraulic oil discharged from the regulator valve 50 as the line pressure PL is generated is supplied to the lubricating oil passage 58b, but the regulator valve is pumped from the mechanical oil pump 42. The primary hydraulic pressure valve, which generates the line pressure, and at the same time the hydraulic pressure discharged from the primary regulator valve. In addition, a secondary regulator valve that discharges at least a part of the hydraulic oil as the secondary pressure is generated may be used, and the hydraulic oil discharged from the secondary regulator valve may be supplied to the lubricating oil passage 58b. In this case, the hydraulic oil may be supplied to the fluid coupling 21 using the secondary pressure generated by the secondary regulator valve.

  In the power transmission device 20 according to the embodiment, the oil passage connected to the output port 114 of the linear solenoid SLC1, the oil passage connected to the discharge port 104 of the electromagnetic pump 100, the oil passage 48 of the clutch C1, and the oil passage 68. Although the switching of the connection between the paths is performed using one switching valve 60, the switching of the connection between these oil paths may be performed using two or more switching valves.

  In the power transmission device 20 of the embodiment, the fluid coupling 21 is provided as an example of the fluid transmission device. However, the power coupling device 21 is not limited to the fluid coupling 21 as long as it can transmit power using a working fluid. A torque converter may be provided instead of the fluid coupling 21.

  In the power transmission device 20 of the embodiment, the switching valve 60 is driven using the line pressure PL. However, the switching valve 60 may be driven using the modulator pressure PMOD obtained by reducing the line pressure PL via a modulator valve (not shown). Alternatively, the line pressure PL and the modulator pressure may be supplied to the switching valve 60 via the solenoid valve and driven using this solenoid valve.

  In the power transmission device 20 according to the embodiment, the automatic transmission 30 with a five-speed shift from the first forward speed to the fifth speed is incorporated. However, the present invention is not limited to this, and a four-speed shift, a six-speed shift, or an eight-speed shift. Any number of automatic transmissions may be incorporated.

  Here, the correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problems will be described. In the embodiment, the engine 22 corresponds to the “motor”, the mechanical oil pump 42 corresponds to the “first pump”, the electromagnetic pump 100 corresponds to the “second pump”, and the regulator valve 50 corresponds to the “regulator”. The switching valve 60 corresponds to a “switching valve”. Further, the signal pressure input port 62a of the switching valve 60 corresponds to a “signal pressure input port”, the input port 62b corresponds to a “first input port”, and the input port 62c corresponds to a “second input port”. The output port 62d corresponds to the “first output port”, and the output port 62e corresponds to the “second output port”. Here, the “prime mover” is not limited to an internal combustion engine that outputs power using a hydrocarbon fuel such as gasoline or light oil, and may be any type of internal combustion engine such as a hydrogen engine, Any type of prime mover may be used as long as it can output power, such as an electric motor other than the internal combustion engine. The “power transmission device” is not limited to the one incorporating the automatic transmission 30 of the forward 1st to 5th gears with 5 gears, and any number of automatic gears such as 4 gears, 6 gears, 8 gears, etc. A transmission may be incorporated. The “second pump” is not limited to an electromagnetic pump that pumps hydraulic oil by electromagnetic force, but generates fluid pressure by driving with electric power, such as an electric pump that pumps hydraulic oil by power from an electric motor. Any type of pump can be used as long as it can be used. Further, the “second pump” is not limited to the pump that pumps the working fluid to the clutch C1 that forms the first forward speed. For example, the gear stage at the start is determined by the driver's instruction or the running state. When is set to a gear position other than the first forward speed (second forward speed, etc.), hydraulic oil may be pumped to the clutch or brake that forms the gear stage. The correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problem is the same as that of the embodiment described in the column of means for solving the problem. It is an example for specifically explaining the best mode for doing so, and does not limit the elements of the invention described in the column of means for solving the problem. That is, the interpretation of the invention described in the column of means for solving the problems should be made based on the description of the column, and the examples are those of the invention described in the column of means for solving the problems. It's just a concrete example

  As mentioned above, although the form for implementing this invention was demonstrated using the Example, this invention is not limited at all to such an Example, In the range which does not deviate from the summary of this invention, it is with various forms. Of course, it can be implemented.

  The present invention is applicable to the automobile industry and the like.

  10 automobile, 12 engine, 14 crankshaft, 16 engine electronic control unit (engine ECU), 20 power transmission device, 21 fluid coupling, 21a coupling chamber, 21b lockup chamber, 22 coupling cover, 22a introduction port, 22b Discharge port, 22c Input / output port, 23 Pump impeller, 24 Turbine runner, 25 Multi-plate lockup clutch, 25a Clutch piston, 25b Clutch plate, 26 Electronic control unit (ATECU) for automatic transmission, 30 Automatic transmission, 30a Double pinion type Planetary gear mechanism, 30b, 30c single pinion planetary gear mechanism, 31a, 31b, 31c sun gear, 32a, 32b, 32c ring gear, 33 a first pinion gear, 33b, 33c pinion gear, 34a second pinion gear, 35a, 35b, 35c carrier, 36 input shaft, 38 output shaft, 40 hydraulic circuit, 41 strainer, 42 mechanical oil pump, 45 manual valve, 45a input port , 45b D (drive) position output port, 45c R (reverse) position output port, 44, 46, 48 Oil passage, 49 Accumulator, 50 Regulator valve, 52 Sleeve, 52a Signal pressure input port, 52b Feedback input port , 52c input port, 52d output port, 52e drain port, 54 spool, 56 spring, 58a, 58b oil passage, 59 bypass valve, 60 switching valve, 62 sleeve, 62a signal pressure input port 62b, 62c input port, 62d, 62e output port, 64 spool, 66 spring, 68 oil passage, 70 modulator valve, 78, 79 oil passage, 80 main electronic control unit, 81 shift lever, 82 shift position sensor, 83 Accelerator pedal, 84 Accelerator pedal position sensor, 85 Brake pedal, 86 Brake switch, 88 Vehicle speed sensor, 90a, 90b Wheel, 92 Differential gear, 94 Drive shaft, 100 Electromagnetic pump, 102 Suction port, 104 Discharge port, 112 Input port 114 output port, 116 drain port, 122 input port, 124 output port, 126 drain port, C1-C3 clutch, B1-B4 brake, F1-F3 one-way clutch, SLC , SLT, SLU linear solenoid.

Claims (6)

A power transmission device including a clutch mounted on a vehicle and transmitting power from a prime mover to an axle,
A first pump that is driven by power from the prime mover to generate and output a fluid pressure;
A second pump that is driven by power supply to generate and output a fluid pressure;
A pressure regulating valve that regulates the working fluid output from the first pump and supplies at least a part of the working fluid discharged along with the regulation to the first lubrication target for lubrication;
When the first pump is driven, the working fluid output from the pressure regulating valve is supplied to the clutch, and the working fluid output from the second pump is used for lubrication as the first lubrication target. A first connection state in which the supply of working fluid from the second pump to the clutch is cut off, and the pressure adjustment when the first pump is not driven. The supply of the working fluid from the valve to the clutch is shut off, and the working fluid output from the second pump is supplied to the clutch, and the working fluid is supplied from the second pump to the second lubrication target. A switching valve for switching between a second connection state in which is cut off,
A power transmission device comprising: The power transmission device according to claim 1,
A fluid transmission device for transmitting power by the working fluid in the working fluid chamber with inflow and outflow of the working fluid in the working fluid chamber;
The second pump supplies a working fluid to the second lubrication target through the working fluid chamber when the switching valve is in the first state.   The switching valve includes a signal pressure input port for inputting the working fluid output from the first pump, a first input port for inputting the working fluid output from the pressure regulating valve, and the second pump. A second input port for inputting the working fluid output from the first output port, a first output port for outputting the working fluid to the clutch, and a second output port for outputting the working fluid to the second lubrication target. And when the fluid pressure is acting on the signal pressure input port, the first input port and the first output port are connected as the first connection state, and the second input port and the The connection to the first output port is cut off, the second input port and the second output port are connected, and when no fluid pressure is acting on the signal pressure input port, the second connection state is established. in front The connection between the first input port and the first output port is cut off, and the second input port and the first output port are connected, and the second input port and the second output port are connected. The power transmission device according to claim 1 or 2, wherein the power transmission device is formed so as to cut off the connection.   The power transmission device according to any one of claims 1 to 3, wherein the second pump is an electromagnetic pump that generates fluid pressure by electromagnetic force.   The power transmission device according to any one of claims 1 to 4, wherein the prime mover is an internal combustion engine capable of automatic stop and automatic start. Prime mover,
The power transmission device according to any one of claims 1 to 5,
Vehicle equipped with.

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