JP5445045B2 - Hydraulic control device for automatic transmission - Google Patents

Description

  The present invention relates to a hydraulic control device that performs shift control in an automatic transmission and performs cooling and lubrication with oil, and in particular, includes a plurality of hydraulic pressure generation sources having different power sources, and operations of hydraulic operation units such as friction engagement devices and movable sheaves. The present invention relates to a hydraulic control device for an automatic transmission that controls a state.

  When a gasoline engine, a diesel engine, or the like is used as a power source, a transmission is usually provided on the output side of the engine. In particular, automatic transmissions in which the shift state is automatically controlled based on the running state of the vehicle are widely used. This automatic transmission includes a stepped automatic transmission in which the gear ratio changes stepwise and a continuously variable transmission in which the gear ratio changes steplessly (that is, continuously). Even in an automatic transmission, hydraulic pressure is widely used for controlling a gear ratio.

  For example, in the case of a stepped automatic transmission, an input clutch for transmitting the output of the engine to the transmission, and a friction engagement device such as a friction clutch or a friction brake for setting the gear position are hydraulic actuators. And is configured to be engaged and released by a hydraulic device such as a hydraulic servo mechanism. In the case of a continuously variable transmission, an input clutch that inputs power to the transmission mechanism is engaged by hydraulic pressure. In particular, in the case of a belt-type continuously variable transmission, the belt is wound around a pulley. In order to change the hook diameter, or to set the pinching force (or pinching force) of the pulley with respect to the belt, a speed change mechanism such as a movable sheave that changes the groove width of the pulley around which the belt is wound is operated by hydraulic pressure. It is configured.

  An oil pump is provided to generate hydraulic pressure when controlling the automatic transmission. This oil pump is generally configured to be driven by the output of the engine. In this case, however, the oil pump stops driving when the engine stops. For example, in a vehicle equipped with a so-called eco-run (or idling stop) system that automatically stops the engine and restarts the engine when the vehicle stops temporarily. When the engine is stopped due to an eco-run or when the engine is restarted, a predetermined oil pressure required for controlling the automatic transmission cannot be secured. In other words, when the engine is automatically stopped during the eco-run, in order to maintain the gear ratio setting that can respond to the subsequent restart, it is specifically engaged / released when setting the gear ratio corresponding to the start. In order to maintain the engagement state of a friction engagement device such as a clutch or a brake, or to maintain the position of the movable sheave for changing the groove width of the pulley at that time, a predetermined value is set in the automatic transmission. It is necessary to maintain the hydraulic pressure.

  Therefore, in a vehicle equipped with the eco-run system as described above, even when the engine is stopped, in order to ensure the hydraulic pressure required for the automatic transmission, In addition to the mechanical oil pump, another oil pump driven by a power source other than the engine, for example, an electric oil pump driven by an output of an electric motor is provided.

  An apparatus having such a configuration in which such an electric oil pump is separately provided is described in Patent Document 1. The hydraulic control device for an automatic transmission described in Patent Document 1 includes a first on-off valve that supplies and shuts off hydraulic pressure from a hydraulic control unit to a C1 clutch as a fail-safe hydraulic circuit, A first check valve that bypasses the first on-off valve and supplies the hydraulic pressure to the C1 clutch when connected in parallel and the first on-off valve is closed, and a minute that drops the hydraulic pressure in the C1 clutch to the drain And an orifice. The fail-safe hydraulic circuit communicates a hydraulic path for supplying hydraulic pressure from the hydraulic control unit to the C1 clutch at normal times, and separates the hydraulic control unit from the C1 clutch when the engine is stopped. The hydraulic pressure from is supplied to the C1 clutch.

  Patent Document 2 discloses an engine automatic stop vehicle in which an engine is temporarily stopped when a predetermined operating condition is satisfied, and an engine that is automatically stopped is restarted when a predetermined operating condition is satisfied. A first hydraulic pressure source that supplies hydraulic pressure to the continuously variable transmission driven by an electric motor, a second hydraulic pressure source that is driven by an electric motor to supply hydraulic pressure to the continuously variable transmission during automatic engine stop, and a first hydraulic pressure source The invention relates to a hydraulic control device for an automatic engine stop vehicle that includes a hydraulic pressure switching valve that is installed in an oil passage between the engine and the continuously variable transmission and opens when the hydraulic pressure of a first hydraulic pressure source rises. Patent Document 2 discloses an example in which the above hydraulic control device is applied to a belt-type continuously variable transmission.

  Patent Document 3 discloses a continuously variable transmission, a multi-stage transmission that performs shifting by selectively engaging and releasing a plurality of friction engagement devices, and supply of hydraulic pressure to the friction engagement devices. A hydraulic control device for an automatic transmission for a vehicle, comprising one or more valves for switching discharge, and a first hydraulic pump for supplying pressure oil to a continuously variable transmission and a friction engagement device. A position that is provided at the pressure oil intake / discharge port of the combined device so that it can be supplied / discharged to or from the valve side from the friction engagement device, and pressure oil from the valve can be supplied to the friction engagement device. A selection valve capable of switching a position for preventing or blocking backflow, and a small-capacity second hydraulic pump provided between the selection valve and the pressure oil suction / discharge port of the friction engagement device The invention relating to the provided hydraulic control device is described. It is. Patent Document 3 describes that an electromagnetic pump that sucks and discharges oil by reciprocating a piston by electromagnetic force is used as the second hydraulic pump.

JP 2002-168330 A JP-A-11-132321 JP 2008-180303 A

  The devices described in each of the above patent documents are all other than the engine, such as an electric oil pump and an electromagnetic oil pump, separately from the mechanical oil pump that is driven by the output of the engine during normal operation to generate hydraulic pressure. An oil pump that is driven by the power source to generate hydraulic pressure is provided. When the engine is stopped during an eco-run, the hydraulic source of the hydraulic circuit that supplies hydraulic pressure to the supply destination such as the friction clutch and friction brake of the automatic transmission is switched from the mechanical oil pump to the electric oil pump. ing. Therefore, even when the engine is stopped, the hydraulic pressure required for the shift control can be stably supplied to the automatic transmission.

  However, when the electric oil pump is installed as an alternative to the mechanical oil pump when the engine is stopped, as in the devices described in the above patent documents, the same capability and function as the existing mechanical oil pump It is necessary to have. In other words, in addition to the mechanical oil pump body, an electric oil pump with a relatively large physique must be provided separately, which causes factors such as an increase in the physique of the entire device and an increase in cost, which in turn improves fuel efficiency. It is an obstruction factor. As described above, when an electric oil pump for generating hydraulic pressure and supplying it to an automatic transmission is installed in place of a normal mechanical oil pump when the engine is stopped, such as during an eco-run, There was still room for improvement in order to suppress the increase in cost and cost.

  The present invention has been made paying attention to the above-mentioned technical problems, and without causing an increase in the size of the apparatus and a significant increase in cost, the hydraulic pressure required for the automatic transmission can be achieved even when the engine is stopped. It is an object of the present invention to provide a hydraulic control device for an automatic transmission that can be supplied efficiently.

In order to achieve the above object, the invention of claim 1 supplies oil to an oil supply section of an automatic transmission connected to a main power source, and sets an operating state of a hydraulic operation section that is operated at the time of shifting. In a hydraulic control device for an automatic transmission for controlling a shift hydraulic pressure for driving, a main oil pump that is driven by an output of the main power source to generate a hydraulic pressure, and a secondary power that can be operated independently of the main power source and a sub oil pump for generating hydraulic pressure is driven by the output of the source, set in communication just before the previous SL hydraulic unit from the main oil pump and the sub oil pump in the feed direction of the hydraulic pressure toward the hydraulic unit vignetting, the main hydraulic based on the discharge pressure or that of the oil pump, the the discharge pressure selectively switching example Bei a switching valve for supplying the hydraulic portion of the sub oil pump, the self The transmission includes a belt-type continuously variable transmission, and the hydraulic actuator includes a movable sheave that changes a groove width of a pulley in the belt-type continuously variable transmission, and a power transmission state in the belt-type continuously variable transmission. The switching valve is provided in communication with the hydraulic oil supply direction from the main oil pump and the sub oil pump to the movable sheave immediately before the movable sheave. It characterized it to contain a sieve switching valve, and the main oil pump and the clutch switching valve provided to communicate immediately before the engagement device from the secondary oil pump in the feed direction of the hydraulic pressure toward the engagement device Is a hydraulic control device for an automatic transmission.

Further, the invention of claim 2, in the invention of claim 1, wherein the switching valve is pre-SL or pressure between the discharge pressure or hydraulic and discharge pressure of the auxiliary oil pump based thereon of the main oil pump as the shift hydraulic The hydraulic control device for an automatic transmission includes a configuration in which one is selected and supplied to the hydraulic operation unit.

  According to a third aspect of the present invention, in the first or second aspect of the present invention, the switching valve includes a first input port to which a discharge pressure of the main oil pump or a hydraulic pressure based thereon is input as the shift hydraulic pressure, and the shift The main oil has a second input port to which the discharge pressure of the auxiliary oil pump is input as hydraulic pressure, an output port that directly communicates with the hydraulic operating portion, and a drain port that discharges the input hydraulic pressure. When the discharge pressure of the pump or the hydraulic pressure based thereon is higher than the discharge pressure of the sub oil pump, the first input port and the output port are communicated and the second input port and the drain port are communicated, When the discharge pressure of the sub oil pump is higher than the discharge pressure of the main oil pump or the hydraulic pressure based thereon, the second input port and the output port are Through and a hydraulic control device for an automatic transmission which comprises a structure of closing the first input port.

According to a fourth aspect of the present invention, in the first aspect of the invention, the sheave switching valve and the clutch switching valve are each input with a hydraulic pressure adjusted based on a discharge pressure of the main oil pump as the shift hydraulic pressure. A first input port, a second input port to which the discharge pressure of the auxiliary oil pump is input as the shifting hydraulic pressure, an output port directly communicating with the engagement device or the movable sheave, and the input hydraulic pressure is discharged. A drain port to be pressurized, a discharge pressure of the main oil pump or a first pilot port to which a hydraulic pressure higher than the transmission hydraulic pressure adjusted based on the discharge pressure is input, and a discharge pressure of the sub oil pump is input and A first pilot port having a second pilot port in which the hydraulic pressure acts in a direction opposite to the hydraulic pressure acting direction in the first pilot port. When the pressure acting on the valve body of the sheave switching valve or the clutch switching valve from the side is larger than the pressure acting on the valve body from the second pilot port side, the first input port and the output port are When the second input port and the drain port communicate with each other and the pressure acting on the valve body from the second pilot port side is greater than the pressure acting on the valve body from the first pilot port side In addition, the hydraulic control device for an automatic transmission includes a configuration in which the second input port communicates with the output port and the first input port is closed.

The invention according to claim 5 is the invention according to any one of claims 1 to 4, further comprising an oil cooler for cooling the oil, wherein the sub oil pump sucks the oil cooled by the oil cooler. A hydraulic control device for an automatic transmission including a configuration for generating hydraulic pressure.

Therefore, when the main power source stops and the main oil pump does not generate hydraulic pressure, the auxiliary oil pump can be driven by the output of the auxiliary power source to generate hydraulic pressure. Even when the main power source is stopped, in an automatic transmission, it is necessary to supply and maintain hydraulic pressure to the hydraulic operating unit in order to set the gear ratio for restarting. According to the first aspect of the present invention, the hydraulic pressure generated by the auxiliary oil pump is directly supplied to the hydraulic operating portion via the switching valve and held. In other words, when the main power source is stopped, an oil passage connecting the sub oil pump and the hydraulic operation unit is selected by the switching valve provided in the immediate vicinity of the hydraulic operation unit, and the sub oil pump and the hydraulic operation unit are connected. Between the two. Therefore, when the hydraulic pressure generated by the sub oil pump instead of the main oil pump is supplied to the hydraulic operating portion, the discharge pressure of the sub oil pump can be directly applied to the hydraulic operating portion. For this reason, the range in which the discharge pressure of the secondary oil pump acts is limited only to the oil passage connecting the hydraulic operation unit and the secondary oil pump, so that compared with the case where hydraulic pressure is supplied to the entire hydraulic circuit of the device, The pump capacity required for the oil pump is small, and the location and amount of oil leakage that inevitably occurs in the circuit is also reduced. As a result, the auxiliary oil pump can be reduced in size and weight, and as a result, the entire apparatus can be reduced in size and weight and cost can be reduced .
When a belt type continuously variable transmission is an object of hydraulic control as an automatic transmission, for example, the operating state of each movable sheave in two sets of pulleys on the driving side and driven side around which the transmission belt is wound, and In addition, it is possible to control the operating state of an engagement device such as a friction clutch or a friction brake used in a forward / reverse switching mechanism or a starting clutch in a belt type continuously variable transmission. Especially in the belt type continuously variable transmission, even when the main power source is stopped, the belt slip when the main power source is started and to realize the groove width of the pulley that sets the gear ratio at the time of restarting. In order to prevent this, it is necessary to supply and maintain the hydraulic pressure to the movable sheave. In this case, according to the first aspect of the present invention, the hydraulic pressure generated by the auxiliary oil pump causes the sheave switching valve to Via, it is directly supplied to the movable sheave and held. In other words, when the main power source stops, the oil passage connecting the sub oil pump and the movable sheave is selected by the sheave switching valve provided in the immediate vicinity of the movable sheave, so that the gap between the sub oil pump and the movable sheave is selected. Is communicated. Therefore, when supplying the hydraulic pressure generated by the sub oil pump instead of the main oil pump to the movable sheave, the discharge pressure of the sub oil pump can be directly applied to the movable sheave. Therefore, when the main power source and the main oil pump are stopped, the necessary oil pressure can be supplied and maintained by the auxiliary oil pump to the movable sheave of the pulley of the belt type continuously variable transmission. The gear ratio can be set appropriately. Since the range in which the discharge pressure of the secondary oil pump acts is limited only to the oil passage connecting the movable sheave and the secondary oil pump, the secondary oil pump is compared with the case where hydraulic pressure is supplied to the entire hydraulic circuit of the device. The pump capacity required for the pump is small, and the location and amount of oil leakage that inevitably occurs in the circuit is also reduced. As a result, the auxiliary oil pump can be reduced in size and weight, and as a result, the entire apparatus can be reduced in size and weight and cost can be reduced.

  According to the invention of claim 2, the discharge pressure of the main oil pump input to the switching valve or the hydraulic pressure based on the discharge pressure, that is, the hydraulic pressure adjusted to a predetermined pressure using the discharge pressure of the main oil pump as a source pressure, The higher one of the discharge pressures of the sub oil pump input to the switching valve is selected, and the selected hydraulic pressure is supplied to the hydraulic pressure operating unit. That is, in the switching valve, the higher working hydraulic pressure is selected from the oil path from the main oil pump to the switching valve and the oil path from the sub oil pump to the switching valve. It is switched so as to communicate with the oil passage leading to the operating part. Therefore, for example, when the main power source is stopped and the oil pressure generation source is switched from the main oil pump to the sub oil pump, the discharge pressure of the sub oil pump becomes higher than the oil pressure on the main oil pump side. The switching valve is automatically switched so that the discharge pressure is supplied to the hydraulic operating part. Therefore, it is possible to easily and reliably switch the hydraulic pressure generation source between the main oil pump and the sub oil pump without performing special control.

  According to the invention of claim 3, the discharge pressure of the main oil pump acting on the first input port of the switching valve or the hydraulic pressure based thereon, that is, the discharge pressure of the main oil pump is adjusted to a predetermined pressure as the original pressure. The higher hydraulic pressure and the discharge pressure of the auxiliary oil pump acting on the second input port of the switching valve are selected, and the selected hydraulic pressure is supplied from the output port of the switching valve to the hydraulic operation unit. The That is, in the switching valve, the higher oil pressure is applied between the oil path from the main oil pump to the first input port of the switching valve and the oil path from the sub oil pump to the second input port of the switching valve. Is selected, and the open / close state of each port is switched so that the selected oil passage communicates with the oil passage from the output port of the switching valve to the hydraulic operation section. Therefore, for example, when the main power source is stopped and the oil pressure generation source is switched from the main oil pump to the sub oil pump, the discharge pressure of the sub oil pump acting on the second input port is the main oil acting on the first input port. By becoming higher than the hydraulic pressure on the pump side, the open / close state of the switching valve is automatically switched so that the discharge pressure of the sub-oil pump is supplied to the hydraulic operation section. Therefore, it is possible to easily and reliably switch the hydraulic pressure generation source between the main oil pump and the sub oil pump without performing special control.

  In addition, when the oil pressure on the main oil pump side is supplied to the hydraulic operating part, the sub oil pump is communicated with the drain port of the switching valve. There is almost no load. As a result, when the hydraulic pressure source is switched between the main oil pump and the sub oil pump, the time during which the sub power source is operated under load can be shortened, and energy consumption in the sub power source is reduced accordingly. be able to.

According to the invention of claim 4 , the clutch switching valve and the sheave switching valve have the first pilot port and the second pilot port in which the hydraulic pressure acts in a direction facing each other. The first pilot port is supplied with a discharge pressure of the main oil pump or a hydraulic pressure higher than the transmission hydraulic pressure adjusted based on the discharge pressure, and the discharge pressure of the sub oil pump is input to the second pilot port of each switching valve. Is done. Therefore, when switching the oil pressure generation source between the main oil pump and the sub oil pump, especially when the main power source is restarted from a stopped state and the oil pressure generation source is switched from the sub oil pump to the main oil pump. The clutch switching valve and the sheave switching valve are switched based on a pilot pressure higher than the transmission hydraulic pressure input to the first pilot port. Therefore, the responsiveness of the switching operation of each switching valve can be improved. In addition, since the hydraulic pressure higher than the transmission hydraulic pressure is used as the pilot pressure, the switching operation of the clutch switching valve and the sheave switching valve can be performed quickly and reliably. It can be prevented or suppressed.

According to the fifth aspect of the present invention, in the sub oil pump, the oil is cooled by the oil cooler and sucks the oil having a relatively high viscosity to generate the oil pressure, so the viscosity is relatively low. The volumetric efficiency of the sub oil pump is improved as compared with the case where hydraulic pressure is generated by oil. In addition, since the viscosity of the oil discharged from the auxiliary oil pump is increased, oil leakage inevitably occurring between the oil passages extending from the auxiliary oil pump to the hydraulic operating portion is reduced. Therefore, the pump capacity required for the auxiliary oil pump is small, and the auxiliary oil pump can be reduced in size and weight accordingly.

It is a schematic diagram for demonstrating the structure of 1st Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the function of the switching valve in the hydraulic control apparatus of this invention. It is a time chart for demonstrating the behavior of each hydraulic pressure at the time of performing an eco-run by the structure of 1st Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the structure of 2nd Example in the hydraulic control apparatus of this invention. It is a time chart for demonstrating the behavior of each hydraulic pressure at the time of performing an eco-run by the structure of 2nd Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the structure of 3rd Example in the hydraulic control apparatus of this invention. It is a time chart for demonstrating the behavior of each oil_pressure | hydraulic at the time of performing an eco-run by the structure of 3rd Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the structure of 4th Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the structure of 5th Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the structure of 6th Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the structure of 7th Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the structure of 8th Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the other structure of the sub oil pump in the hydraulic control apparatus of this invention.

  The hydraulic control device according to the present invention is mainly mounted on a vehicle and changes a torque transmission path by appropriately engaging and releasing a friction engagement device such as a friction clutch or a brake to change a predetermined transmission speed. A stepped automatic transmission to be set, or a belt type continuously variable transmission that continuously (steplessly) changes the gear ratio by changing the pulley groove width around which the belt is wound by operating the movable sheave of the pulley. Alternatively, a toroidal type that continuously changes the gear ratio by sandwiching a power roller between a pair of disks arranged opposite to each other and displacing a torque transmission point between the power roller and each disk ( Alternatively, it is intended for hydraulic control of an automatic transmission such as a traction type continuously variable transmission. That is, the present invention is directed to a hydraulic control device for an automatic transmission that performs hydraulic control when the operation state of the friction engagement device, the movable sheave, or the power roller as described above is controlled by hydraulic pressure.

Specifically, hydraulic control system for an automatic transmission is targeted in the present invention, as a hydraulic sources, for example, a driving force source of the vehicle, the main power source automatic transmission is consolidated output Is driven by the output of a sub-power source that is independent of the main power source and can be operated and controlled independently of the main power source. And a secondary oil pump for generating the oil. During normal operation, that is, when the main power source is in operation, hydraulic pressure is generated by the main oil pump, and when the main power source is stopped, hydraulic pressure is generated by the auxiliary oil pump. The oil discharged from the oil pump is supplied to a hydraulic operating part of the automatic transmission and an oil supply part that requires oil for lubrication and cooling. A more detailed configuration of the hydraulic control device for an automatic transmission that is the subject of the present invention will be described based on the following specific example.

(First embodiment)
FIG. 1 shows a part of a hydraulic circuit in a hydraulic control unit HCU of an automatic transmission which is a subject of the present invention as a first embodiment of the present invention. In FIG. 1, reference numeral 1 denotes a main power source in the present invention. Here, an example for an internal combustion engine such as a gasoline engine, a diesel engine, or an LPG engine will be described. In the following description, the main power source 1, that is, the internal combustion engine 1 is referred to as an engine 1.

  An input shaft (not shown) of an automatic transmission is connected to the output side of the engine 1 via, for example, a torque converter (not shown), and the rotor shaft (or input shaft) of the mechanical oil pump 2 is connected. ) 2a is connected.

  The mechanical oil pump 2 is driven by transmission of output torque of the engine 1 as a driving force source to generate hydraulic pressure, and obtains output torque of the engine 1 to drive the rotor shaft 2a. Thus, the oil is sucked from the suction port 2i, and the sucked oil is discharged from the discharge port 2o. That is, it corresponds to the main oil pump of the present invention.

  As the pump mechanism of the mechanical oil pump 2, for example, a rotary pump such as a gear pump, a trochoid pump, a vane pump, a screw pump, or a known pump having various configurations such as a piston pump can be employed. The mechanical oil pump 2 sucks oil stored in an oil pan 3 provided at the bottom of a casing (not shown), for example, and discharges it from a discharge port 2o.

  The discharge port 2o of the mechanical oil pump 2 communicates with an oil supply unit 4 of an automatic transmission that needs to be cooled and lubricated with oil, and is connected via a control valve 5, a manual valve 6, and a select valve 7. And communicated with the hydraulic operating portion 8 of the automatic transmission.

  The oil supply unit 4 is, for example, an oil supply mechanism or a bearing (not shown) in the automatic transmission, when the automatic transmission is driven by the power of the engine 1 being transmitted while the vehicle is running. It is a part that needs to be cooled and lubricated by. Therefore, when the operation of the engine 1 is stopped while the vehicle is stopped and the driving of the automatic transmission is stopped accordingly, the oil supply unit 4 can temporarily stop the oil supply. Part.

  The control valve 5 is a pressure regulating valve that regulates (specifically, depressurizes) the hydraulic pressure supplied to the hydraulic operating portion 8, that is, the shift hydraulic pressure in the present invention, during the shift control of the automatic transmission. The input port 5i communicates with the discharge port 2o side of the mechanical oil pump 2, and the output port 5o communicates with the input port 6i of the adjacent manual valve 6. For example, it is operated by a signal pressure supplied from a solenoid valve (not shown) or the like, and the transmission hydraulic pressure is appropriately adjusted and controlled.

  The manual valve 6 is a switching valve that operates in conjunction with, for example, a shift lever (not shown) of an automatic transmission, and the position of the spool is switched by a signal pressure supplied from, for example, a solenoid valve (not shown). Correspondingly, each range of the automatic transmission is switched. The output port 6 o is communicated with the hydraulic operation unit 8 via the select valve 7.

  The select valve 7 corresponds to the switching valve of the present invention, and is provided in the immediate vicinity of the hydraulic operating unit 8 in the oil path from the mechanical oil pump 2 and the electric oil pump 10 described later to the hydraulic operating unit 8. The hydraulic pressure adjusted using the discharge pressure of the mechanical oil pump 2 as the original pressure and the discharge pressure of the electric oil pump 10 are selectively switched and supplied to the hydraulic operation unit 8. . The detailed configuration of the select valve 7 will be described later together with the electric oil pump 10.

  The hydraulic operation unit 8 corresponds to the hydraulic operation unit of the present invention. For example, in a stepped automatic transmission, a friction clutch that is operated in an engaged / released state when setting a predetermined shift stage, Friction engagement device such as friction clutch or friction clutch to transmit / cut off power transmission between friction brake or vehicle driving force source and automatic transmission, or changing groove width of pulley of belt type continuously variable transmission For example, a movable sheave that can be operated for the automatic transmission, and a hydraulic actuator that is operated to change the attitude of the power roller of the toroidal-type continuously variable transmission. This is the part where the release and operating states are controlled.

  In addition, when the vehicle is stopped, the automatic transmission mounted on the vehicle needs to set a gear stage or a gear ratio at which the vehicle can start in preparation for a subsequent restart. For this reason, even when the vehicle is stopped, it is necessary to keep the hydraulic pressure necessary to set a predetermined gear position (speed ratio) for re-starting continuously acting on the hydraulic operating unit 8. In other words, the hydraulic operation unit 8 is configured so that the oil supply unit 4 that can temporarily stop the supply of oil when the stopped engine 1 is stopped, even when the stopped engine 1 is stopped. In other words, it is a part that requires the supply of hydraulic pressure, or that needs to hold the supplied hydraulic pressure.

  Therefore, when performing a so-called eco-run that temporarily stops the operation of the engine 1 such as when the vehicle is temporarily stopped, such as when waiting for a signal, the mechanical oil pump 2 is driven by another power source instead of the engine 1. Alternatively, it is necessary to provide an oil pump separate from the mechanical oil pump 2 that is driven by another power source instead of the engine 1 and generates hydraulic pressure.

  For this purpose, a power source that can operate independently of the engine 1, that is, an electric motor (Motor) 9 corresponding to the auxiliary power source in the present invention is provided as another power source in place of the engine 1. An electric oil pump 10 corresponding to the sub oil pump in the present invention is provided on the output side of the electric motor 9. That is, the rotor shaft (or input shaft) 10 a of the electric oil pump 10 is connected to the output side of the electric motor 9.

  The electric oil pump 10 is driven by the transmission of the output torque of the electric motor 9 as a driving force source, and generates hydraulic pressure, and obtains the output torque of the electric motor 9 to drive the rotor shaft 10a. Thus, the oil is sucked from the suction port 10i, and the sucked oil is discharged from the discharge port 10o. As the pump mechanism of the electric oil pump 10, as in the case of the mechanical oil pump 2 described above, for example, a rotary pump such as a gear pump, a trochoid pump, a vane pump, a screw pump, or various configurations such as a piston pump are known. The pump can be adopted. The electric oil pump 10 also sucks oil stored in an oil pan 3 provided at the bottom of a casing (not shown), for example, and discharges it from the discharge port 10o.

  The discharge port 10o of the electric oil pump 10 is not in communication with the oil supply unit 4 described above, but is in direct communication with the hydraulic operation unit 8 of the automatic transmission through only the select valve 7. As described above, the oil supply unit 4 can temporarily stop the supply of oil when the stopped engine 1 is stopped. Therefore, when the stopped engine 1 is stopped, it is sufficient to keep supplying the hydraulic pressure necessary for maintaining the speed ratio at the time of restart only to the hydraulic operating unit 8 at least, or the speed ratio at the time of restart is set. What is necessary is just to hold | maintain the hydraulic pressure required in order to maintain. Focusing on this, in the hydraulic control device HCU in the present invention, the supply destination of the oil by the electric oil pump 10 is limited to the hydraulic operation unit 8 as described above, so that the electric motor 9 and the electric oil pump 10 can be controlled. The size and weight are reduced.

  The select valve 7 is a so-called Max Select type switching valve that selects the high pressure of the hydraulic pressures input from the two systems and supplies it to the output side. Specifically, the select valve 7 includes first and second input ports 7a and 7b, and first and second pilot ports 7c and 7d corresponding to the input ports 7a and 7b. Output port 7o and drain port 7e. As a hydraulic pressure supply system on the mechanical oil pump 2 side, an output port 6o of the manual valve 6 is communicated with the first input port 7a and the first pilot port 7c. On the other hand, the discharge port 10o of the electric oil pump 10 communicates with the second input port 7b and the second pilot port 7d as a hydraulic pressure supply system on the electric oil pump 10 side. The hydraulic operation unit 8 communicates with the output port 7o.

  The select valve 7 is configured so that the position of a spool (not shown) is switched according to the hydraulic pressure acting on the pilot ports 7c and 7d. Specifically, when the hydraulic pressure acting on the first pilot port 7c is higher than the hydraulic pressure acting on the second pilot port 7d, the spool is moved to the second pilot port 7d side ( The first input port 7a communicates with the output port 7o, and the second input port 7b communicates with the drain port 7e.

  When the hydraulic pressure acting on the second pilot port 7d is higher than the hydraulic pressure acting on the first pilot port 7c, the spool acts on the first pilot port 7c side (FIG. 1) due to the hydraulic pressure acting on the second pilot port 7d. The second input port 7b and the output port 7o are communicated with each other and the first input port 7a is closed.

  Accordingly, the select valve 7 is a portion where the oil passage from the mechanical oil pump 2 to the hydraulic operation portion 8 and the oil passage from the electric oil pump 10 to the hydraulic operation portion 8 merge, The discharge pressure of the mechanical oil pump 2 is provided at a location immediately before the section 8 and the hydraulic pressure with the discharge pressure of the mechanical oil pump 2 as the original pressure is higher than the discharge pressure of the electric oil pump 10. The hydraulic pressure as the original pressure is supplied to the hydraulic operating unit 8 and the oil discharged from the electric oil pump 10 is discharged from the drain port 7e. On the contrary, the discharge pressure of the electric oil pump 10 is When the discharge pressure is higher than the original pressure, the hydraulic pressure generated by the electric oil pump 10 is supplied to the hydraulic operating section 8 and the oil path from the mechanical oil pump 2 to the hydraulic operating section 8 is shut off. Configuration to You have me.

  An electronic control unit (ECU) 11 for electrically controlling the solenoid valve or the electric motor 9 in the hydraulic control unit HCU is provided. The electronic control unit 11 is mainly composed of a microcomputer as an example, and performs an operation according to a predetermined program based on input data, data stored in advance, etc., and the operation state of the solenoid valve or the electric motor 9 is determined. It is configured to perform control. Further, for the electronic control unit 11, detection signals from, for example, an oil temperature sensor (not shown) for detecting the temperature of the oil and a rotation speed sensor (not shown) for detecting the rotation speed of each rotating member are received. It is designed to be entered.

  Thus, apart from the mechanical oil pump 2 that is driven by the output of the engine 1 to generate hydraulic pressure, the electric oil pump 10 that is driven by the output of the electric motor 9 to generate hydraulic pressure is provided, and these mechanical oil pumps are provided. By connecting the hydraulic pressure supply system on the second side and the hydraulic pressure supply system on the electric oil pump 10 side to the hydraulic operating unit 8 via the so-called Max Select type select valve 7 as described above, mechanical oil is supplied. The higher one of the hydraulic pressure adjusted using the discharge pressure of the pump 2 as the original pressure and the discharge pressure of the electric oil pump 10 is automatically selected, and the hydraulic pressure of the supply system on the selected side is supplied to the hydraulic operation unit 8. Can be supplied.

  That is, as shown in FIG. 2 (a), when the mechanical oil pump 2 is driven by the output of the engine 1 during operation of the engine 1 to generate hydraulic pressure, the mechanical oil pump The hydraulic pressure (referred to as clutch pressure) Pc adjusted with the discharge pressure of 2 as the original pressure becomes higher than the discharge pressure Pm of the electric oil pump 10. Therefore, in the select valve 7, the hydraulic pressure (that is, the clutch pressure Pc) that acts on the first pilot port 7c is higher than the hydraulic pressure that acts on the second pilot port 7d (that is, the discharge pressure Pm). A force is applied to the spool 7 to push it toward the second pilot port 7d (the right side in FIG. 2). Therefore, the spool moves to the second pilot port 7d side, and the first input port 7a and the output port 7o are connected. The second input port 7b is communicated with the drain port 7e. As a result, the clutch pressure Pc on the mechanical oil pump 2 side is supplied to the hydraulic actuator 8 via the manual valve 6 and the select valve 7.

  When the mechanical oil pump 2 is driven, the electric oil pump 10 does not need to be driven, so the discharge pressure Pm of the electric oil pump 10 is zero. Even if the electric oil pump 10 is driven to generate hydraulic pressure, the maximum value of the discharge pressure Pm is set lower than the clutch pressure Pc on the mechanical oil pump 2 side. In a state where the clutch pressure Pc is stably generated by being driven, “Pc> Pm”. Further, when the hydraulic oil is generated by driving the electric oil pump 10 in this state, the hydraulic pressure from the electric oil pump 10 is discharged from the drain port 7e of the select valve 7, so that the electric oil pump 10 Does little work. That is, almost no load is applied to the electric motor 9, and the amount of power consumption is extremely small.

  FIG. 2B shows a state in which the mechanical oil pump 2 is driven by the output of the engine 1 and the hydraulic pressure is supplied to the hydraulic operation unit 8 as described above. In this state, the electric oil pump 10 is driven by the output of the electric motor 9 and the hydraulic pressure is supplied to the hydraulic operation unit 8.

  That is, when the electric motor 9 is operated when the engine 1 is stopped and the electric oil pump 10 is driven by the output of the electric motor 9 to generate hydraulic pressure, the discharge pressure Pm of the electric oil pump 10 is mechanical. It becomes higher than the clutch pressure Pc on the oil pump 2 side. Therefore, in the select valve 7, the hydraulic pressure (that is, the discharge pressure Pm) that acts on the second pilot port 7d is higher than the hydraulic pressure that acts on the first pilot port 7c (that is, the clutch pressure Pc). The force which presses it to the 1st pilot port 7c side (left side in FIG. 2) acts on 7 spools. Therefore, the spool moves to the first pilot port 7c side, and the second input port 7b and the output port 7o are connected. The first input port 7a and the drain port 7e are closed. As a result, the discharge pressure Pm of the electric oil pump 10 is supplied to the hydraulic operation unit 8 only through the select valve 7.

  When hydraulic pressure is supplied to the hydraulic operation unit 8 by driving the mechanical oil pump 2 described above, in the oil passage from the mechanical oil pump 2 to the hydraulic operation unit 8, the periphery of the control valve 5 and the manual valve 6. Inevitable oil leakage occurs. Further, for example, unless a switching valve or a stop valve is specially provided, the hydraulic pressure generated by the mechanical oil pump 2 is also supplied to the oil supply unit 4 in the automatic transmission. However, oil leakage inevitably occurs.

On the other hand, when the electric oil pump 10 is driven and the hydraulic pressure is supplied to the hydraulic operation unit 8 as described above, the hydraulic pressure generated by the electric oil pump 10 is the second input of the select valve 7. The oil is directly supplied to the hydraulic actuator 8 through the port 7b and the output port 7o. Therefore, in the oil passage from the electric oil pump 10 to the hydraulic operation unit 8, oil leakage inevitably occurs only in the vicinity of the select valve 7. That is, as compared with the case of supplying the hydraulic pressure generated in mechanical oil pump 2 during the operation engine 1 to the hydraulic unit 8, the hydraulic oil pressure which is generated by the electric oil pump 10 when the engine 1 is stopped When supplying to the part 8, inevitable oil leakage is reduced. Therefore, the pump capacity required for the electric oil pump 10 is small, and the electric oil pump 10 can be reduced in size and weight accordingly.

  As described above, for example, when performing an eco-run, a state in which the mechanical oil pump 2 is driven to supply the hydraulic pressure to the hydraulic operating unit 8 and a state in which the electric oil pump 10 is driven to supply the hydraulic pressure to the hydraulic operating unit 8 FIG. 3 is a time chart showing changes in the oil pressure and the like when switching between and. In FIG. 3, when the eco-run is started at time t0, the operation of the engine 1 is stopped and the operation command Pm_com (broken line) for the electric motor 9 is output. As the rotational speed Ne (one-dot chain line) of the engine 1 decreases, the actual pressure actually acts on the clutch pressure Pc (two-dot chain line) using the discharge pressure of the mechanical oil pump 2 as an original pressure and the hydraulic operation unit 8. Although the hydraulic pressure Pc_real (solid line) decreases, the actual hydraulic pressure Pc_real switches from the clutch pressure Pc to the discharge pressure Pm at time t1 when the clutch pressure Pc becomes lower than the discharge pressure Pm of the electric oil pump 10.

  Thereafter, when the operation of the engine 1 is resumed to end the eco-run, the clutch pressure Pc increases as the engine speed Ne increases. At time t2 when the clutch pressure Pc becomes higher than the discharge pressure Pm of the electric oil pump 10, the actual hydraulic pressure Pc_real is switched from the discharge pressure Pm to the clutch pressure Pc. Then, at time t3 when the engine speed Ne returns to the normal idling speed, the operation command Pm_com of the electric motor 9 is canceled, and the eco-run ends.

  Switching between the clutch pressure Pc and the discharge pressure Pm as described above is automatically switched according to the magnitude relationship between the clutch pressure Pc and the discharge pressure Pm when the select valve 7 functions as described above. . Therefore, it is possible to easily switch the source of hydraulic pressure between the mechanical oil pump 2 and the electric oil pump 10 without performing any particular control and without providing a complicated configuration and mechanism. it can.

(Second embodiment)
FIG. 4 shows a part of a hydraulic circuit in a second embodiment of the hydraulic control unit HCU of the automatic transmission according to the present invention. In the example shown in FIG. 4, with respect to the select valve 7 in the configuration of the first embodiment described above, the hydraulic oil supply system on the side of the mechanical oil pump 2 and the hydraulic operating unit 8 when the electric oil pump 10 is not operated. This is an example of a configuration using a select valve 12 having a spring 12s that presses a spool at a position where the valve is communicated. The configuration of the other parts is basically the same as that shown in FIG. 1 in the first embodiment. Therefore, in the following description, the same reference numerals as those in the previous drawings are attached to the same components as those described in the previous drawings, and detailed description thereof will be omitted. Moreover, description of the oil supply part 4, the electronic control apparatus 11, etc. is also abbreviate | omitted.

  In FIG. 4, the select valve 12 in the configuration of the second embodiment corresponds to the switching valve of the present invention, similar to the select valve 7 described above, and includes a mechanical oil pump 2 and an electric oil pump 10. The hydraulic pressure that is provided in the immediate vicinity of the hydraulic operating section 8 in the oil path from the hydraulic operating section 8 to the hydraulic operating section 8 is adjusted with the discharge pressure of the mechanical oil pump 2 as the original pressure, and the discharge pressure of the electric oil pump 10. Are selectively switched and supplied to the hydraulic operation unit 8.

  The select valve 12 is a switching valve of a type that selects one of the hydraulic pressures input from the two systems and supplies it to the output side, and includes two input ports 12a and 12b and their respective input ports. Two pilot ports 12c and 12d corresponding to 12a and 12b, an output port 12o, and a drain port 12e are provided. As a hydraulic pressure supply system on the mechanical oil pump 2 side, the output port 6o of the manual valve 6 is communicated with the first input port 12a and the first pilot port 12c. On the other hand, the discharge port 10o of the electric oil pump 10 communicates with the second input port 12b and the second pilot port 12d as a hydraulic pressure supply system on the electric oil pump 10 side. The hydraulic operation unit 8 communicates with the output port 12o.

  A spring 12s is provided on the spool to apply a pressing force from the first pilot port 12c to the second pilot port 12d. That is, the spring 12s is an elastic member that applies an elastic force to the spool in a direction of pressing the spool from the first pilot port 12c to the second pilot port 12d.

  Therefore, when the combined pressure of the hydraulic pressure acting on the first pilot port 12c and the pressure corresponding to the elastic force of the spring 12s is higher than the hydraulic pressure acting on the second pilot port 12d, the select valve 12 is synthesized. The spool is pressed to the second pilot port 12d side (right side in FIG. 4) by the pressure, the first input port 12a and the output port 12o are communicated, and the second input port 12b and the drain port 12e are communicated. .

  On the other hand, when the hydraulic pressure acting on the second pilot port 12d is higher than the combined pressure of the hydraulic pressure acting on the first pilot port 12c and the pressure corresponding to the elastic force of the spring 12s, the second pilot port 12d The spool is pressed to the first pilot port 12c side (left side in FIG. 4) by the acting hydraulic pressure, the second input port 12b and the output port 12o are communicated, and the first input port 12a is closed.

That is, if the hydraulic pressure acting on the first pilot port 12c, that is, the clutch pressure on the mechanical oil pump 2 side is Pc, the discharge pressure of the electric oil pump 10 is Pm, and the pressure corresponding to the elastic force of the spring 12s is Ps. Since the combined pressure of the clutch pressure Pc on the mechanical oil pump 2 side and the pressure Ps corresponding to the elastic force of the spring 12s is “Pc + Ps”, the pressure regulating formula in the select valve 12 is
Pc + Ps = Pm
It becomes.

Therefore, the magnitude relationship between the combined pressure “Pc + Ps” and the discharge pressure Pm is
Pc + Ps> Pm
In this case, the spool of the select valve 12 moves to the second pilot port 12d side, and the first input port 12a and the output port 12o are communicated with each other so that the hydraulic pressure Pc using the discharge pressure of the mechanical oil pump 2 as the original pressure is obtained. This is supplied to the hydraulic operation unit 8. The magnitude relationship between the combined pressure “Pc + Ps” and the discharge pressure Pm is
Pc + Ps <Pm
In this case, the spool of the select valve 12 moves to the first pilot port 12c side, and the hydraulic pressure generated by the electric oil pump 10, that is, the electric oil pump 10 is communicated with the second input port 12b and the output port 12o. The discharge pressure Pm is supplied to the hydraulic operation unit 8.

  In the configuration of the second embodiment, the state in which the mechanical oil pump 2 is driven to supply the hydraulic pressure to the hydraulic operating unit 8, and the state in which the electric oil pump 10 is driven to supply the hydraulic pressure to the hydraulic operating unit 8 FIG. 5 is a time chart showing changes in the hydraulic pressures and the like when switching between. As in the case of the first embodiment shown in FIG. 3, when the eco-run is started at time t0, the operation of the engine 1 is stopped and the operation command Pm_com (broken line) for the electric motor 9 is output. Is done. As the rotational speed Ne (one-dot chain line) of the engine 1 decreases, the clutch pressure Pc (two-dot chain line) on the mechanical oil pump 2 side and the actual hydraulic pressure Pc_real (solid line) actually acting on the hydraulic operation unit 8 are increased. descend.

  In the configuration of the second embodiment, the time t4 when the clutch pressure Pc becomes lower than the discharge pressure Pm of the electric oil pump 10 and the actual oil pressure Pc_real switches from the clutch pressure Pc to the discharge pressure Pm is the elasticity of the spring 12s. Since the pressure Ps corresponding to the force acts on the first pilot port 12c side, it is later than the time t1 in the first embodiment. On the other hand, the operation of the engine 1 is resumed to end the eco-run thereafter, the clutch pressure Pc increases as the engine speed Ne increases, and the clutch pressure Pc on the mechanical oil pump 2 side becomes the electric oil pump. The time t5 at which the actual hydraulic pressure Pc_real is switched from the discharge pressure Pm to the clutch pressure Pc when the discharge pressure Pm is higher than the pressure 10 is likewise the pressure Ps corresponding to the elastic force of the spring 12s acting on the first pilot port 12c side. However, it is earlier than the time t2 in the first embodiment.

  Therefore, in the configuration of the second embodiment, the period from time t4 to time t5 when the discharge pressure Pm of the electric oil pump 10 becomes the actual hydraulic pressure Pc_real acting on the hydraulic operation unit 8 is the same as that of the first embodiment. In this case, the discharge pressure Pm of the electric oil pump 10 becomes shorter than the period from the time t1 to the time t2 when the actual hydraulic pressure Pc_real acting on the hydraulic pressure operating unit 8 is achieved. That is, the time during which the electric oil pump 10 is operated under load is shortened.

  Therefore, according to the configuration of the second embodiment, the load operation time of the electric oil pump 10 can be shortened and the power consumption of the electric motor 9 can be reduced when the eco-run is executed. Further, when returning from the eco-run, the oil pressure generating source is switched from the electric oil pump 10 to the mechanical oil pump 2 at an early stage, that is, while the rotational speed of the engine 1 is low. Switching delays can be prevented. During normal operation of the engine 1, an oil passage from the mechanical oil pump 2 to the hydraulic operating unit 8 is reliably formed by the elastic force of the spring 12 s, so that the pressure loss during clutch pressure control is reduced. In addition, the control response can be improved.

(Third embodiment)
FIG. 6 shows a part of a hydraulic circuit in a third embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. In the example shown in FIG. 6, with respect to the select valve 7 in the configuration of the first embodiment described above, the hydraulic oil supply system on the side of the electric oil pump 10 and the hydraulic operating unit 8 when the electric oil pump 10 is not operated. It is an example of the structure using the select valve 13 which has the spring 13s which presses a spool in the position which communicates.

  In FIG. 6, the select valve 13 in the configuration of the third embodiment corresponds to the switching valve of the present invention, similar to the select valve 7 described above, and includes the mechanical oil pump 2 and the electric oil pump 10. The hydraulic pressure that is provided in the immediate vicinity of the hydraulic operating section 8 in the oil path from the hydraulic operating section 8 to the hydraulic operating section 8 is adjusted with the discharge pressure of the mechanical oil pump 2 as the original pressure, and the discharge pressure of the electric oil pump 10. Are selectively switched and supplied to the hydraulic operation unit 8.

  The select valve 13 is a switching valve of a type that selects one of the hydraulic pressures input from the two systems and supplies it to the output side, and the first and second input ports 13a and 13b. And first and second pilot ports 13c and 13d corresponding to the input ports 13a and 13b, an output port 13o, and a drain port 13e. As a hydraulic pressure supply system on the mechanical oil pump 2 side, the output port 6o of the manual valve 6 is communicated with the first input port 13a and the first pilot port 13c. On the other hand, the discharge port 10o of the electric oil pump 10 communicates with the second input port 13b and the second pilot port 13d as a hydraulic pressure supply system on the electric oil pump 10 side. The hydraulic operation unit 8 communicates with the output port 13o.

  A spring 13s that applies a pressing force from the second pilot port 13d to the first pilot port 13c is provided on the spool. That is, the spring 13s is an elastic member that applies an elastic force to the spool in a direction of pressing the spool from the second pilot port 13d to the first pilot port 13c.

  Therefore, when the hydraulic pressure acting on the first pilot port 13c is higher than the combined pressure of the hydraulic pressure acting on the second pilot port 13d and the pressure corresponding to the elastic force of the spring 13s, the select valve 13 The spool is pressed to the second pilot port 13d side (the right side in FIG. 6) by the hydraulic pressure acting on the first pilot port 13c, the first input port 13a and the output port 13o communicate with each other, and the second input port 13b and the drain The port 13e is communicated. On the other hand, when the combined pressure of the hydraulic pressure acting on the second pilot port 13d and the pressure corresponding to the elastic force of the spring 13s is higher than the hydraulic pressure acting on the first pilot port 13c, the second pilot port 13d The spool is pressed to the first pilot port 13c side (left side in FIG. 6) by the combined pressure of the acting hydraulic pressure and the pressure corresponding to the elastic force of the spring 13s, and the second input port 13b and the output port 13o communicate with each other. And the first input port 13a is closed.

That is, the hydraulic pressure acting on the first pilot port 13c, that is, the clutch pressure on the mechanical oil pump 2 side is Pc, the discharge pressure of the electric oil pump 10 is Pm, and the pressure corresponding to the elastic force of the spring 13s is Ps. The combined pressure of the discharge pressure Pm on the electric oil pump 10 side and the pressure Ps corresponding to the elastic force of the spring 13 s is “Pm + Ps”.
Pc = Pm + Ps
It becomes.

Therefore, the magnitude relationship between the clutch pressure Pc and the combined pressure “Pm + Ps” is
Pc> Pm + Ps
In this case, the spool of the select valve 13 moves to the second pilot port 13d side, and the first input port 13a and the output port 13o are communicated with each other so that the clutch pressure Pc on the mechanical oil pump 2 side is transferred to the hydraulic operation unit 8. Will be supplied. The magnitude relationship between the clutch pressure Pc and the combined pressure “Pm + Ps” is
Pc <Pm + Ps
In this case, the spool of the select valve 13 moves toward the first pilot port 13c, and the hydraulic pressure generated by the electric oil pump 10, that is, the electric oil pump 10 is communicated with the second input port 13b and the output port 13o. The discharge pressure Pm is supplied to the hydraulic operation unit 8.

  In the configuration of the third embodiment, a state in which the mechanical oil pump 2 is driven to supply the hydraulic pressure to the hydraulic operating unit 8, and a state in which the electric oil pump 10 is driven to supply the hydraulic pressure to the hydraulic operating unit 8 Changes in the hydraulic pressures and the like when switching are shown in the time chart of FIG. As in the case of the first embodiment shown in FIG. 3, when the eco-run is started at time t0, the operation of the engine 1 is stopped and the operation command Pm_com (broken line) for the electric motor 9 is output. Is done. As the rotational speed Ne (one-dot chain line) of the engine 1 decreases, the clutch pressure Pc (two-dot chain line) on the mechanical oil pump 2 side and the actual hydraulic pressure Pc_real (solid line) actually acting on the hydraulic operation unit 8 are increased. descend.

  In the configuration of the third embodiment, the time when the clutch pressure Pc on the mechanical oil pump 2 side becomes lower than the discharge pressure Pm of the electric oil pump 10 and the actual oil pressure Pc_real is switched from the clutch pressure Pc to the discharge pressure Pm. t6 is earlier than the time t1 in the first embodiment by the amount that the pressure Ps corresponding to the elastic force of the spring 13s acts on the second pilot port 13d side. That is, the actual hydraulic pressure Pc_real is quickly switched from the clutch pressure Pc to the discharge pressure Pm.

  On the other hand, the operation of the engine 1 is resumed to end the eco-run thereafter, the clutch pressure Pc increases as the engine speed Ne increases, and the clutch pressure Pc on the mechanical oil pump 2 side becomes the electric oil pump. At time t7 when the actual hydraulic pressure Pc_real is switched from the discharge pressure Pm to the clutch pressure Pc because the pressure is higher than the discharge pressure Pm of 10, the pressure Ps corresponding to the elastic force of the spring 13s is similarly applied to the second pilot port 13c side. However, it is later than the time t2 in the first embodiment. That is, the actual hydraulic pressure Pc_real is reliably switched from the discharge pressure Pm to the clutch pressure Pc after the clutch pressure Pc has sufficiently increased.

  As described above, according to the configuration of the third embodiment, when the eco-run is executed, the hydraulic pressure source is quickly switched from the mechanical oil pump 2 to the electric oil pump 10, and at the end of the eco-run, The oil pressure generation source can be reliably switched from the hydraulic oil pump 10 to the mechanical oil pump 2. Therefore, it is possible to always switch the oil pressure generation source on the safe side against slipping of the clutch or pulley caused by insufficient oil pressure of the oil supplied to the hydraulic operation unit 8, and as a result, the reliability of the automatic transmission Can be improved.

(Fourth embodiment)
FIG. 8 shows a part of a hydraulic circuit in a fourth embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. Example shown in FIG. 8, the suction side of the electric Oirupon flop 10, which is an example of a configuration in which an oil cooler 14 for cooling the oil. FIG. 8 shows a configuration example in which the oil cooler 14 in the fourth embodiment is added to the configuration of the second embodiment shown in FIG. 4 (that is, the configuration using the select valve 12). 1, the structure which added the oil cooler 14 in this 4th Example to the structure using the select valves 7 and 13 in the 1st, 3rd Example shown in FIG. 6 may be sufficient.

  In FIG. 8, an oil cooler 14 for cooling the oil is provided on the suction side of the electric oil pump 10. Specifically, an oil cooler 14 is disposed in the middle of an oil path connecting the oil pan 3 and the electric oil pump 10, and the suction port 10 i of the electric oil pump 10 and the discharge port 14 o of the oil cooler 14 are connected to each other. It is communicated. The suction port 14 i of the oil cooler 14 communicates with the oil pan 3 directly or indirectly.

  The oil cooler 14 is configured to cool the oil sucked in or carried in from the suction port 14i and to discharge or carry it out from the discharge port 14o. As an oil cooling method of the oil cooler 14, for example, Various types such as an air-cooled type, a water-cooled type, and a heat exchange type can be adopted.

  Thus, by providing the oil cooler 14 on the suction side of the electric oil pump 10, when the electric oil pump 10 is driven to generate hydraulic pressure, the electric oil pump 10 always has the oil cooler 14. Oil that has been cooled in the air will be inhaled. That is, the electric oil pump 10 sucks oil having a relatively high viscosity after being cooled by the oil cooler 14 and generates hydraulic pressure. As a result, the volumetric efficiency of the electric oil pump 10 is improved as compared with the case where the oil pressure is generated by sucking oil having a relatively low viscosity. Therefore, the pump capacity required for the electric oil pump 10 is small, and the electric oil pump 10 can be reduced in size and weight accordingly.

(5th Example)
FIG. 9 shows a part of a hydraulic circuit in a fifth embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. Example shown in FIG. 9, the configuration of the fourth embodiment described above which is provided an oil cooler 14 to the suction side of the electric Oirupon flop 10, the suction of the oil of the electric oil pump 10 in response to the temperature of the oil It is an example of the structure which further added the temperature-sensitive type switching valve which switches the origin.

  In FIG. 9, a temperature-sensitive switching valve 15 is provided in the middle of an oil passage connecting the oil pan 3 and the oil cooler 14 and the electric oil pump 10. Specifically, the oil pan 3 and the first input port 15a of the sensitive temperature switching valve 15 are communicated, and the discharge port 14o of the oil cooler 14 and the second input port 15b of the temperature sensitive switching valve 15 are connected. It is communicated. The output port 15o of the temperature sensitive switching valve 15 and the suction port 10i of the electric oil pump 10 are communicated with each other.

  The temperature-sensitive switching valve 15 has the first and second input ports 15a and 15b and the output port 15o as described above, and connects the first input port 15a and the output port 15o. And a state in which the second input port 15b and the output port 15o communicate with each other can be selectively switched. The temperature-sensitive switching valve 15 further includes, for example, a temperature-sensitive spring 15s formed by using a function such as a shape memory alloy or thermowax, and the first input according to the oil temperature. It is configured to switch between a state in which the port 15a and the output port 15o are in communication and a state in which the second input port 15b and the output port 15o are in communication.

  More specifically, when the oil temperature of the oil discharged from the oil cooler 14 is higher than a predetermined value, the temperature-sensitive switching valve 15 is in a state where the first input port 15a and the output port 15o are in communication with each other. On the contrary, when the oil temperature of the oil discharged from the oil cooler 14 is lower than a predetermined value, the second input port 15b and the output port 15o are in communication with each other. Here, the predetermined value is a value set in advance in consideration of, for example, the average oil temperature in the automatic transmission during normal operation or the cooling characteristics of the oil in the oil cooler 14 during cold operation.

  Therefore, in the configuration of the fifth embodiment, the function of the temperature-sensitive switching valve 15 selects the electric oil having the lower oil temperature out of the oil in the oil pan 3 and the oil discharged from the oil cooler 14 to be electrically operated. Can be supplied to the suction port 10 i of the oil pump 10. That is, in the electric oil pump 10, oil with a relatively high viscosity can always be sucked to generate hydraulic pressure, and the volumetric efficiency of the electric oil pump 10 can be improved. Therefore, the pump capacity required for the electric oil pump 10 is small, and the electric oil pump 10 can be reduced in size and weight accordingly.

(Sixth embodiment)
FIG. 10 shows a part of a hydraulic circuit in a sixth embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. Normally, when an oil cooler is provided, an oil passage that bypasses the oil cooler is provided in order to prevent overcooling of the oil in the oil cooler. In order to automatically switch the oil inflow destination between the bypass oil passage and the oil cooler according to the oil temperature, for example, a temperature-sensitive switching mechanism using a thermostat or the like is also provided. The example shown in FIG. 10 is an example of a configuration that uses an existing temperature-sensitive switching mechanism.

In FIG. 10, a switching valve 16 is provided in the middle of an oil passage connecting the oil pan 3 and the oil cooler 14 and the electric oil pump 10. Specifically, it has passed the first input port 16a communicated to the oil pan 3 and the switching valve 16 is passed through the second input port 16b are communicated in the discharge port 14o and the switching valve 16 of the oil cooler 14 Yes. The output port 16o of the switching valve 16 and the suction port 10i of the electric oil pump 10 are communicated with each other.

  The switching valve 16 acts on the first and second input ports 16a and 16b, the output port 16o, the pilot port 16p to which an external pilot pressure is input, and the pilot port 16p as described above. A spring 16s for applying an elastic force in a direction opposite to the hydraulic pressure, the first input port 16a and the output port 16o being in communication with each other, and the second input port 16b and the output port 16o being in communication with each other; It is configured to be able to selectively switch between the two states.

  Therefore, when the pilot pressure acting on the pilot port 16p is larger than the pressure corresponding to the elastic force of the spring 16s, the switching valve 16 is in a state where the first input port 16a and the output port 16o are in communication with each other. Conversely, when the pilot pressure acting on the pilot port 16p is smaller than the pressure corresponding to the elastic force of the spring 16s, the second input port 16b and the output port 16o are in communication with each other. .

On the other hand, on the suction side of the oil cooler 14, a state in which the oil flows into the oil cooler 14 and a state in which the oil does not flow into the oil cooler 14 and is bypassed to a bypass oil path (not shown) are set to the oil temperature. A cooler bypass valve 17 is provided for automatically switching in response. The cooler bypass valve 17 includes , for example, a thermostat (not shown) configured using functions such as bimetal and thermowax, and the oil temperature on the suction side of the oil cooler 14 is lower than a predetermined value. It is configured to open when it is low and to divert the oil to a detour oil passage or the like. Accordingly, the input port 17 i of the cooler bypass valve 17 communicates directly or indirectly with the oil pan 3. Further, the output port 17o of the cooler bypass valve 17 communicates with a bypass oil passage or the like.

  In the configuration of the sixth embodiment, the function of the thermostat of the existing cooler bypass valve 17 as described above is used to operate the switching valve 16 according to the oil temperature. The output port 17o and the pilot port 16p of the switching valve 16 are in communication.

  Therefore, when the oil temperature on the suction side of the oil cooler 14 is lower than a predetermined value, the cooler bypass valve 17 is opened, and the hydraulic pressure discharged from the output port 17o becomes a pilot pressure to the pilot port 16p of the switching valve 16. Works. Therefore, the switching valve 16 is set in a state in which the first input port 16a and the output port 16o communicate with each other when a predetermined pilot pressure acts on the pilot port 16p. That is, oil that bypasses the oil cooler 14 is supplied to the suction port 10 i of the electric oil pump 10.

  On the other hand, when the oil temperature on the suction side of the oil cooler 14 is higher than a predetermined value, the cooler bypass valve 17 is not opened and the hydraulic pressure is not discharged from the output port 17o. That is, the pilot pressure does not act on the pilot port 16p of the switching valve 16. Therefore, the switching valve 16 is set in a state where the second input port 16b and the output port 16o communicate with each other. That is, the oil cooled by the oil cooler 14 and discharged from the discharge port 14 o is supplied to the suction port 10 i of the electric oil pump 10.

  Therefore, in the configuration of the sixth embodiment, the thermostat function of the existing cooler bypass valve 17 is used, and the oil temperature of the oil pan 3 and the oil discharged from the oil cooler 14 is lower. Oil, that is, oil having a high viscosity can be selected and supplied to the suction port 10 i of the electric oil pump 10. That is, without providing a special configuration, oil with a relatively high viscosity can always be drawn into the electric oil pump 10 to generate hydraulic pressure, and the volumetric efficiency of the electric oil pump 10 can be improved. be able to. Therefore, the pump capacity required for the electric oil pump 10 is small, and the electric oil pump 10 can be reduced in size and weight accordingly.

(Seventh embodiment)
FIG. 11 shows a part of a hydraulic circuit in a seventh embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. The example shown in FIG. 11 is a configuration example in the case where a belt type continuously variable transmission is used as a control target, particularly as an automatic transmission to be controlled in the present invention. In the configuration shown in FIG. 11, for example, the engine 1, the mechanical oil pump 2, the electric motor 9, the electric oil pump 10, or the like having the same configuration as that described in the previous drawing, the previous drawing. The same reference numerals are attached and detailed description is omitted. Moreover, description of the oil supply part 4, the electronic control apparatus 11, etc. is also abbreviate | omitted.

  In FIG. 11, reference numerals 18 and 19 denote the movable sheave 18 and the clutch 19 corresponding to the hydraulic operation part of the present invention when the controlled object in the present invention is a belt type continuously variable transmission. The belt type continuously variable transmission to be used here has a known configuration that is conventionally mounted on a vehicle, and includes two sets of pulleys on the driving side and the driven side, and the power transmitted by being wound around these pulleys. A transmission mechanism including a transmission belt for performing the above is provided. In addition, since the speed change mechanism composed of these pulleys and the transmission belt and the engine 1 that is the main power source cannot be reversed in their own rotational directions, in a normal belt type continuously variable transmission, A forward / reverse switching mechanism is provided for switching and setting the forward speed and the reverse speed. Furthermore, instead of a torque converter that has been widely adopted in conventional automatic transmissions, a starting mechanism constituted by a friction clutch can be provided.

  Each of the pulleys on the driving side and the driven side is provided with a movable sheave that moves back and forth in the rotation axis direction of the pulley in order to change the groove width of each pulley or the clamping pressure of each pulley against the transmission belt. . Further, the forward / reverse switching mechanism is, for example, connected to a planetary gear mechanism and rotating elements in the planetary gear mechanism or by preventing rotation of any of the rotating elements so as to be in a directly connected state (that is, a forward gear). ) And a change state (that is, reverse gear), and a friction clutch and a friction brake. In addition, the starting mechanism may be constituted by a friction clutch as described above.

  The front and rear operations of the movable sheave of each pulley in the pulley rotation axis direction, and the engagement / release operations of the friction clutch and friction brake of the forward / reverse switching mechanism or the friction clutch of the starting mechanism are all controlled by hydraulic pressure. It is configured as follows. Therefore, in the configuration shown in FIG. 11, the movable sheave 18 indicates the movable sheave in the driving pulley and the driven pulley of the belt-type continuously variable transmission, and is the hydraulic operating portion in the present invention. It corresponds to a movable sheave. The clutch 19 indicates a friction clutch and a friction brake in the forward / reverse switching mechanism, a friction clutch in the start mechanism, and the like, and is a hydraulic operation part in the present invention, and particularly corresponds to the clutch in the present invention. is there.

  Accordingly, the movable sheave 18 is supplied with hydraulic pressure from the mechanical oil pump 2 or the electric oil pump 10 via the select valve 20. Similarly, the hydraulic pressure from the mechanical oil pump 2 or the electric oil pump 10 is supplied to the clutch 19 via the select valve 21.

  Both the select valves 20 and 21 in the configuration of the seventh embodiment correspond to the switching valve of the present invention, similar to the above-described select valves 7 and 12 and the like. This corresponds to the sheave switching valve in the present invention, and the select valve 21 corresponds to the clutch switching valve in the present invention.

  The select valve 20 is provided in the immediate vicinity of the movable sheave 18 in the oil passage from the mechanical oil pump 2 and the electric oil pump 10 to the movable sheave 18, and adjusts the discharge pressure of the mechanical oil pump 2 as the original pressure. The hydraulic pressure and the discharge pressure of the electric oil pump 10 are selectively switched and supplied to the movable sheave 18. The select valve 21 is provided in the immediate vicinity of the movable sheave 19 in the oil path from the mechanical oil pump 2 and the electric oil pump 10 to the clutch 19, and the discharge pressure of the mechanical oil pump 2 is used as the original pressure. The pressure is adjusted and the discharge pressure of the electric oil pump 10 is selectively switched and supplied to the movable sheave 18.

  The select valve 20 and the select valve 21 are switching valves of the type in which either one of the hydraulic pressures input from the two systems is selected and supplied to the output side, like the above-described select valves 7, 12 and the like. Each of the two input ports 20a and 20b and the input ports 21a and 21b, and the two pilot ports 20c and 20d and the pilot ports 21c corresponding to the input ports 20a and 20b and the input ports 21a and 21b, respectively. 21d, an output port 20o and an output port 21o, and a drain port 20e and a drain port 21e.

  As a hydraulic pressure supply system on the mechanical oil pump 2 side, the output port 5o of the control valve 5 is connected to the first input ports 20a, 21a and the first pilot ports 20c, 21c of the select valves 20, 21, respectively. Yes. On the other hand, as a hydraulic pressure supply system on the electric oil pump 10 side, the discharge port 10o of the electric oil pump 10 is connected to the second input ports 20b and 21b and the second pilot ports 20d and 21d of the select valves 20 and 21, respectively. Communication is made via check valves 22 and 23, respectively.

  The check valves 22 and 23 allow oil to flow from the electric oil pump 10 side to the select valves 20 and 21, respectively, and conversely, the oil from the select valves 20 and 21 side to the electric oil pump 10. This is a one-way valve that stops the flow, and is intended to prevent backflow when the hydraulic pressure acting on the movable sheave 18 or the clutch 19 becomes high.

  Further, the movable sheave 18 and the clutch 19 are communicated with the output ports 20o and 21o of the select valves 20 and 21, respectively. Then, springs 20s and 21s for applying a pressing force from the first pilot ports 20c and 21c to the second pilot ports 20d and 21d are provided on the spools of the select valves 20 and 21, respectively. In other words, the springs 20s and 21s are elastic members that apply an elastic force to the spool in a direction of pressing the spools from the first pilot ports 20c and 21c to the second pilot ports 20d and 21d, respectively.

  Therefore, each of these select valves 20, 21 has a combined pressure of the hydraulic pressure acting on the first pilot ports 20c, 21c and the pressure corresponding to the elastic force of the springs 20s, 21s, respectively. Is higher than the hydraulic pressure acting on the second pressure, the spool is pressed to the second pilot port 20d, 21d side (lower side in FIG. 11) by the combined pressure, and the first input port 20a, 21a and the output port 20o, 21o And the second input ports 20b and 21b and the drain ports 20e and 21e are respectively communicated. Therefore, in this case, the hydraulic pressure generated by the mechanical oil pump 2, specifically, the hydraulic pressure adjusted by the control valve 5 based on the discharge pressure of the mechanical oil pump 2 is supplied to the movable sheave 18 and the clutch 19. Will be.

  On the other hand, if the hydraulic pressure acting on the second pilot ports 20d, 21d is higher than the combined pressure of the hydraulic pressure acting on the first pilot ports 20c, 21c and the pressure corresponding to the elastic force of the springs 20s, 21s, The spool is pressed toward the first pilot ports 20c, 21d (upper side in FIG. 11) by the hydraulic pressure acting on the second pilot ports 20d, 21d, and the second input ports 20b, 21b and the output ports 20o, 21o are The first input ports 20a and 21a are respectively closed and closed. Therefore, in this case, the hydraulic pressure generated by the electric oil pump 10, that is, the discharge pressure of the electric oil pump 10 is supplied to the movable sheave 18 and the clutch 19.

  Thus, according to the configuration of the seventh embodiment, when the belt-type continuously variable transmission is the target of hydraulic control, the movable sheave 18 of each pulley on the driving side and the driven side in the belt-type continuously variable transmission. And the operating state of an engagement device such as a friction clutch or a friction brake used in a forward / reverse switching mechanism or a starting mechanism in the belt type continuously variable transmission can be appropriately controlled. That is, for example, even when the engine 1 is stopped when the eco-run is executed and the mechanical oil pump 2 does not generate hydraulic pressure, the source of hydraulic pressure is switched from the mechanical oil pump 2 to the electric oil pump 10, The hydraulic pressure generated by the electric oil pump 10 is directly supplied to and held by the movable sheave 18 and the clutch 19 via select valves 20 and 21 provided in the immediate vicinity of the movable sheave 18 and the clutch 19, respectively. Is done.

  Accordingly, when the engine 1 is stopped, for example, when an eco-run is performed, the electric oil pump 10, the movable sheave 18, and the clutch 19 are selected by the select valves 20 and 21 provided in the immediate vicinity of the movable sheave 18 and the clutch 19, respectively. Is connected, and the electric oil pump 10 and the movable sheave 18 and the clutch 19 are communicated with each other. Therefore, when the hydraulic pressure generated by the electric oil pump 10 instead of the mechanical oil pump 2 is supplied to the movable sheave 18 and the clutch 19, the discharge pressure of the electric oil pump 10 is directly applied to the movable sheave 18 and the clutch 19. Can act. In particular, when the engine 1 and the mechanical oil pump 2 are stopped during an eco-run, the necessary oil pressure is supplied and maintained by the electric oil pump 2 to the movable sheave 18 of the pulley of the belt-type continuously variable transmission. Therefore, the required gear ratio can be set appropriately at the time of restart after the end of the eco-run.

  Further, as described above, the select valves 20 and 21 are provided in the immediate vicinity of the movable sheave 18 and the clutch 19, respectively, so that the discharge pressure of the mechanical oil pump 2 becomes low, or the mechanical oil pump 2 is When the hydraulic pressure is not generated by stopping, there is no need to provide a check valve for preventing the backflow of the hydraulic pressure from the movable sheave 18 and the clutch 19 side to the mechanical oil pump 2. When the discharge pressure of the mechanical oil pump 2 decreases and the discharge pressure of the electric oil pump 10 becomes higher than the hydraulic pressure adjusted based on the discharge pressure of the mechanical oil pump 2, the select valves 20 and 21 are electrically driven. Since the oil path is quickly switched so as to select the oil path connecting the hydraulic oil pump 10 to the movable sheave 18 and the clutch 19, it is not necessary to consider the backflow of hydraulic pressure from the movable sheave 18 and the clutch 19 side to the mechanical oil pump 2. Because.

Generally, in a belt-type continuously variable transmission mounting tower in vehicles, for example, in the case when towing the vehicle, i.e., the vehicle in all states in which the power source has stopped the vehicle travels, the belt type continuously variable transmission In order to prevent seizure of gears, bearings and the like on the drive pulley side, the oil leakage inevitably generated from each movable sheave 18 is more movable on the driven pulley side than the oil leakage amount on the movable sheave 18 on the drive pulley side. The amount of oil leakage in the sheave 18 is increased. As more oil leaks from the movable sheave 18 on the driven pulley side, the belt-type continuously variable transmission shifts to the speed increasing side during towing travel, and the rotational speed of the drive pulley decreases. Therefore, seizure of gears, bearings, and the like on the drive pulley side can be prevented, and the durability of the belt type continuously variable transmission is ensured.

  Therefore, in order to prevent backflow when the mechanical oil pump 2 is stopped, if a check valve is provided between the movable sheave 18 on the driven pulley side and the mechanical oil pump 2 in particular, the movable sheave 18 on the driven pulley side Oil leakage is not allowed, and the rotational speed of the drive pulley cannot be reduced as described above. On the other hand, since the check valves can be eliminated by providing the select valves 20 and 21 as described above, the durability of the belt-type continuously variable transmission is ensured as described above when towing. be able to.

(Eighth embodiment)
FIG. 12 shows part of a hydraulic circuit in an eighth embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. The example shown in FIG. 12 is a modification of the above-described seventh embodiment, and the pilot pressure input to the first pilot ports 20c, 21c of the select valves 20, 21 in the configuration of the seventh embodiment is changed. It is an example. Therefore, in the configuration shown in FIG. 12, those having the same configuration as that described in the previous drawing are given the same reference numerals as those in the previous drawing, and detailed description thereof is omitted. Moreover, description of the oil supply part 4, the electronic control apparatus 11, etc. is also abbreviate | omitted.

  In FIG. 12, the first pilot ports 20c and 21c of the select valves 20 and 21 in the configuration of the eighth embodiment are communicated with the discharge port 10c of the mechanical oil pump 2 through oil passages 24 and 25, respectively. . Therefore, in the configuration of the eighth embodiment, the hydraulic pressure input to the first input ports 20a, 21a of the select valves 20, 21 to the first pilot ports 20c, 21c of the select valves 20, 21, that is, a mechanical oil pump The discharge pressure of the mechanical oil pump 2 higher than the transmission hydraulic pressure (clutch pressure) adjusted based on the discharge pressure 2 can be input as the pilot pressure.

  Thus, according to the configuration of the eighth embodiment, the first pilot ports 20c, 21c of the select valves 20, 21 are regulated using the discharge pressure of the mechanical oil pump 2 or the discharge pressure as the original pressure. The hydraulic pressure higher than the changed hydraulic pressure is input, and the discharge pressure of the electric oil pump 10 is input to the second pilot ports 20d and 21d of the select valves 20 and 21. Therefore, when the hydraulic pressure source is switched between the mechanical oil pump 2 and the electric oil pump 10, in particular, the engine 1 is restarted from a stopped state, and the hydraulic pressure source is switched from the electric oil pump 10. When switching to the mechanical oil pump 2, the switching operation of the select valves 20, 21 is performed based on a pilot pressure higher than the transmission hydraulic pressure input to the first pilot ports 20 c, 21 c of the select valves 20, 21. Will be.

  Therefore, the responsiveness of the switching operation of these select valves 20 and 21 can be improved. Furthermore, by making the hydraulic pressure higher than the transmission hydraulic pressure, specifically, the discharge pressure of the mechanical oil pump 2 as a pilot pressure, the switching operation of the select valves 20 and 21 can be performed quickly and reliably. Generation | occurrence | production of the valve stick etc. in these select valves 20 and 21 can be prevented or suppressed.

  In the configuration shown in the eighth embodiment and the configuration shown in the seventh embodiment, the oil cooler 14 in the configuration shown in the fourth to sixth embodiments can be applied. By doing so, also in the configuration shown in the eighth embodiment and the configuration shown in the seventh embodiment, the electric oil pump is the same as in the configuration shown in the fourth to sixth embodiments. The volumetric efficiency of the electric oil pump 10 can be reduced. Therefore, the pump capacity required for the electric oil pump 10 can be reduced, and the electric oil pump 10 can be reduced in size and weight accordingly.

  Further, the present invention is not limited to the specific examples described above. For example, in the configuration of each of the embodiments described above, the electric oil pump 10 provided as the auxiliary oil pump of the present invention applies a basic structure of a conventional general solenoid valve as shown in FIG. Can be replaced by a pump 26 (so-called valve pump, solenoid pump, solenoid valve pump, etc.) configured to generate Briefly describing the configuration, in FIG. 13, the valve pump 26 includes a coil portion 26 c provided with an electromagnetic coil 27, check valves 28 and 29 that restrict oil flow in one direction, and oil A valve (pump) portion 26v configured by an oil chamber 30 and the like in which suction and discharge are performed, and a plunger 26p that reciprocates in the oil chamber 30 are configured.

  The check valve 28 allows oil to flow from the suction port 26 i into the oil chamber 30 at the suction port 26 i of the valve pump 26, and conversely, flows oil from the oil chamber 30 to the outside of the suction port 26 i. It becomes the structure which stops. The check valve 29 allows oil to flow from the oil chamber 30 to the outside of the discharge port 26o at the discharge port 26o of the valve pump 26, and conversely, the oil from the discharge port 26o to the oil chamber 30 is allowed to flow. It is the structure which stops the flow of. The plunger 26p is configured to reciprocate in the oil chamber 30 by the action of the electromagnetic force of the electromagnetic coil 27.

  By controlling the current supplied to the electromagnetic coil 27, the plunger 26p can be reciprocated at high speed in the oil chamber 30. Therefore, along with the reciprocating operation of the plunger 26p, the oil can be repeatedly sucked and discharged in the oil chamber 30, so that the valve pump 26 can function as a reciprocating volume pump.

  By applying such a valve pump 26 as an auxiliary oil pump in the present invention, the configuration of the apparatus is simpler than that in the case of using an electric oil pump 10 including, for example, a brushless rotary motor as a power source. And can be reduced in size and weight.

  In the above specific examples, the stepped automatic transmission and the belt type continuously variable transmission are described as examples of the automatic transmission targeted by the present invention. For example, as described above, Also, a toroidal (or traction type) continuously variable transmission can be used. Alternatively, the present invention can be applied to a hydraulic control of a so-called semi-automatic transmission in which a shift operation in a manual transmission is automatically controlled by a predetermined hydraulic operation mechanism.

  DESCRIPTION OF SYMBOLS 1 ... Engine (main power source), 2 ... Mechanical oil pump (main oil pump), 4 ... Oil supply part, 7, 12, 13, 20, 21 ... Select valve (switching valve), 8 ... Hydraulic operation part, DESCRIPTION OF SYMBOLS 9 ... Electric motor (sub power source), 10 ... Electric oil pump (sub oil pump), 11 ... Electronic control unit (ECU), 14 ... Oil cooler, 18 ... Movable sheave, 19 ... Clutch (engagement device), HCU ... Hydraulic control device.

Claims (5)

In a hydraulic control device for an automatic transmission that supplies oil to an oil supply unit of an automatic transmission connected to a main power source and controls a shift hydraulic pressure for setting an operation state of a hydraulic operation unit that is operated at the time of shifting,
A main oil pump driven by the output of the main power source to generate hydraulic pressure;
A sub oil pump driven by the output of a sub power source operable independently of the main power source to generate hydraulic pressure;
The main oil pump and the setting in communication just before the auxiliary oil from said pump hydraulic portion before Symbol hydraulic unit in the feed direction of the hydraulic pressure for the vignetting, and oil pressure based on the discharge pressure or that of the main oil pump, wherein a discharge pressure selectively switching example Bei a switching valve for supplying the hydraulic portion of the sub oil pump,
The automatic transmission includes a belt type continuously variable transmission,
The hydraulic operation unit includes a movable sheave that changes a groove width of a pulley in the belt-type continuously variable transmission, and an engagement device involved in change control of a power transmission state in the belt-type continuously variable transmission,
The switching valve includes a sheave switching valve provided in communication with the main oil pump and the sub oil pump in front of the movable sheave in a hydraulic pressure supply direction toward the movable sheave, the main oil pump, and the sub oil valve. A clutch switching valve provided in communication with the oil pump immediately before the engagement device in a hydraulic pressure supply direction toward the engagement device.
Hydraulic control apparatus for an automatic transmission, wherein the this.   The switching valve includes a configuration in which either the discharge pressure of the main oil pump or the hydraulic pressure based thereon or the discharge pressure of the sub oil pump is selected and supplied to the hydraulic operation unit. The hydraulic control device for an automatic transmission according to claim 1. The switching valve is
A first input port to which the discharge pressure of the main oil pump or a hydraulic pressure based thereon is input as the shift hydraulic pressure; a second input port to which the discharge pressure of the sub oil pump is input as the shift hydraulic pressure; An output port that directly communicates with the drain port, and a drain port that discharges the input hydraulic pressure,
When the discharge pressure of the main oil pump or the hydraulic pressure based thereon is higher than the discharge pressure of the sub oil pump, the first input port and the output port are communicated, and the second input port and the drain port are connected. Communication, the second input port and the output port are connected and the first input port is closed when the discharge pressure of the sub oil pump is higher than the discharge pressure of the main oil pump or the hydraulic pressure based thereon The hydraulic control device for an automatic transmission according to claim 1, wherein the hydraulic control device includes: Said sheet over blanking switching valve and the clutches switching valve, respectively,
A first input port to which a hydraulic pressure adjusted based on a discharge pressure of the main oil pump is input as the shift hydraulic pressure; a second input port to which the discharge pressure of the sub oil pump is input as the shift hydraulic pressure; An output port that directly communicates with the engagement device or the movable sheave, a drain port that discharges the input hydraulic pressure, and a hydraulic pressure that is higher than the discharge pressure of the main oil pump or the shift hydraulic pressure that is adjusted based on the discharge pressure. A first pilot port, and a second pilot port to which a discharge pressure of the auxiliary oil pump is input and a hydraulic pressure acts in a direction opposite to a hydraulic pressure acting direction in the first pilot port,
When the pressure acting on the valve body of the sheave switching valve or the clutch switching valve from the first pilot port side is larger than the pressure acting on the valve body from the second pilot port side, the first input port and The pressure that acts on the valve body from the second pilot port side acts on the valve body from the first pilot port side, and communicates the output port and the second input port and the drain port. 2. The hydraulic control device for an automatic transmission according to claim 1, further comprising a configuration in which the second input port communicates with the output port and closes the first input port when the pressure is larger than the pressure . An oil cooler for cooling the oil;
Before SL sub Oirupon flop, the hydraulic control device for the automatic transmission according to any one of claims 1 to 4, characterized in that it comprises an arrangement for generating a hydraulic pressure to suck the cooled oil by the oil cooler.

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