JP5316108B2 - Hydraulic control device for automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic control device for an automatic transmission for efficiently supplying oil pressure necessary in the automatic transmission during economy running without causing enlargement or cost increase. <P>SOLUTION: The hydraulic control device HCU of an automatic transmission supplying oil to an oil supply part 4 of the automatic transmission, and controlling and supplying speed change oil pressure setting an operating state of a hydraulic actuation part 7 actuated in speed change includes a main oil pump 2 generating oil pressure by output of a main power source 1, communicating a main discharge port 2o with the oil supply part 4, and communicating the main discharge port 2o with the hydraulic actuation part 7 via a speed change control valve 6, a sub oil pump 9 generating oil pressure by output of a sub power source 8 and communicating a sub discharge port 9o with the hydraulic actuation part 7, and oil pressure holding mechanisms 5, 10 holding the oil pressure acting on the hydraulic actuation part 7 when the oil pressure is supplied to the hydraulic actuation part 7 from the sub oil pump 9. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

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 two hydraulic pressure generation sources having different power sources, and includes hydraulic operation units such as a friction engagement device and a movable sheave. The present invention relates to a hydraulic control device for an automatic transmission that controls an operation state.

  When an engine such as a gasoline engine or a diesel engine 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 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 a machine, hydraulic pressure is widely used for controlling the gear ratio.

  For example, in the case of a stepped automatic transmission, a friction engagement device such as an input clutch for transmitting engine output to the transmission or a clutch or a brake for setting a shift stage is provided by a hydraulic actuator or hydraulic pressure. It is configured to be engaged and released by a hydraulic device such as a 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 pulley clamping force (or pinching force) on 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 a hydraulic pressure for 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 vehicles equipped with a so-called eco-run (or idling stop) system that automatically stops and restarts the engine when temporarily stopped, When the engine is stopped due to the engine or when the engine is restarted, a predetermined oil pressure required for controlling the automatic transmission cannot be secured. That is, when the engine is automatically stopped at the time of eco-run, in order to maintain a gear ratio that can respond to the subsequent start, specifically, a clutch that is 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 brake 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 hydraulic pressure is applied in the automatic transmission. It is necessary to keep it.

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

  Patent Document 1 discloses an apparatus having a configuration in which an electric oil pump for assisting the function of such a mechanical oil pump is separately provided. The hydraulic pressure control device for an automatic transmission described in Patent Document 1 is a fail-safe hydraulic circuit, which is provided in parallel with a first on-off valve for supplying and shutting off hydraulic pressure from a hydraulic control unit to a C1 clutch, and a first on-off valve. A first check valve that bypasses the first on-off valve and supplies the hydraulic pressure to the C1 clutch when the first on-off valve is fixed in a closed state, and a micro orifice that drops the hydraulic pressure in the C1 clutch to the drain And. The fail-safe hydraulic circuit communicates a hydraulic path for supplying hydraulic pressure from the hydraulic control unit to the C1 clutch during normal operation, and separates the hydraulic control unit and the C1 clutch from the electric hydraulic pump when the engine is stopped. The hydraulic pressure is supplied to the C1 clutch.

  Patent Document 2 discloses that a mechanical pump that is mechanically driven by a vehicle engine to generate hydraulic pressure, and that the hydraulic pressure generated by the mechanical pump is supplied to the friction engagement device that performs shifting. A mechanical hydraulic line that leads to a pressure regulating valve that discharges, an electric pump that is electrically driven to generate hydraulic pressure, and the mechanical hydraulic line are provided independently of each other, and regulates the hydraulic pressure generated by the electric pump. The electric hydraulic line that is directly supplied to the mechanical hydraulic line immediately before the valve and the hydraulic pressure generated by the electric pump are prevented from flowing back to the mechanical pump through the mechanical hydraulic line, and the hydraulic pressure generated by the mechanical pump is electrically An invention relating to a hydraulic control device for an automatic transmission provided with backflow prevention means for preventing backflow through the hydraulic line to the electric pump side is described. In Patent Document 2, when the discharge pressure of the mechanical pump is insufficient, such as when the engine is started, or when the hydraulic pressure for realizing the gear stage required for starting is insufficient during idle stop, such as during an eco-run operation, Activating an electric pump is disclosed.

  Patent Document 3 discloses an engine automatic stop vehicle in which an engine is temporarily stopped when a predetermined operation condition is satisfied, and an engine that is automatically stopped is restarted when a predetermined operation 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 3 discloses an example in which the above hydraulic control device is applied to a belt-type continuously variable transmission.

  Patent Document 4 discloses an eco-run control for automatically stopping / restarting the engine when a predetermined condition of the vehicle is satisfied, and driving an electric oil pump that generates hydraulic pressure to be supplied to the automatic transmission when the engine is stopped by the eco-run control. A control device that performs control, and is connected to a sensor that provides data used to determine the environment and / or vehicle state around the vehicle stop position when the engine is stopped by eco-run control. Based on the data from the sensor An invention relating to a control device configured to perform drive control of an electric oil pump is described.

  Patent Document 5 discloses a continuously variable transmission, a multi-stage transmission that performs a shift 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 Invention relating to provided hydraulic control device is described It has been. Patent Document 5 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 2007-270991 A JP-A-11-132321 JP 2007-46634 A JP 2008-180303 A

  The devices described in each of the above patent documents are all other than engines such as electric oil pumps and electromagnetic oil pumps, apart from mechanical oil pumps that generate hydraulic pressure by being driven by engine output in normal times. An oil pump that is driven by the power source to generate hydraulic pressure is provided. When the engine is stopped during the eco-run, the hydraulic source of the hydraulic circuit that supplies the hydraulic pressure to the supply destination such as the friction engagement device of the automatic transmission is switched from the mechanical oil pump to the electric oil pump. Yes. 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 An electric oil pump with Therefore, it is necessary to separately provide an electric oil pump including an electric motor in addition to the oil pump main body, which causes factors such as an increase in the size and cost of the entire device, which in turn impedes an improvement in fuel efficiency. Yes. In this way, when the engine is stopped, such as during an eco-run, an electric oil pump that generates hydraulic pressure and supplies it to the automatic transmission instead of the normal mechanical oil pump is installed separately. There was still room for improvement in order to suppress it.

  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 that controls and supplies variable hydraulic pressure, a main discharge port that is driven by the output of the main power source to generate hydraulic pressure and discharges oil by the hydraulic pressure communicates with the oil supply section. And a main oil pump whose main discharge port communicates with the hydraulic pressure operating part via a shift control valve for controlling the shift hydraulic pressure, and an output of a sub-power source operable independently of the main power source A sub-oil pump that is driven by the hydraulic pressure and generates a hydraulic pressure, and a sub-discharge port that discharges oil by the hydraulic pressure directly communicates with the hydraulic pressure-operating portion; When the hydraulic pressure is supplied, a hydraulic holding mechanism for holding the hydraulic pressure acting on the said hydraulic unit, said Bei example a pressure detecting means for detecting a delivery pressure of the auxiliary oil pump is supplied to the hydraulic unit When switching the oil pressure generation source from the main oil pump to the sub oil pump, the operation of the main power source is performed after the discharge pressure of the sub oil pump is increased to a predetermined lower limit oil pressure required by the hydraulic operation section. a hydraulic control device for an automatic transmission which is characterized that you stopped.

According to a second aspect of the present invention, in the first aspect of the invention, the hydraulic pressure holding mechanism is provided between the main discharge port and the speed change control valve, and is directed from the main discharge port to the speed change control valve. And a first check valve that allows oil to flow only in the cylinder, and is provided between the sub-discharge port and the hydraulic operation unit, and allows oil flow only in the direction from the sub-discharge port to the hydraulic operation unit. A hydraulic control device for an automatic transmission including a second check valve.

The invention of claim 3 further comprises a pressure adjusting mechanism for adjusting the hydraulic pressure supplied from the sub oil pump to the hydraulic operating section to a predetermined set hydraulic pressure in the invention of claim 1 or 2. 1 is a hydraulic control device for an automatic transmission.

According to a fourth aspect of the present invention, in the third aspect of the invention, the pressure regulating mechanism includes a relief valve that opens and drains the drain port when the discharge pressure of the sub oil pump exceeds the set hydraulic pressure. This is a hydraulic control device for an automatic transmission.

According to a fifth aspect of the present invention, in the first aspect of the present invention, the hydraulic operation unit includes a movable sheave that operates during a shift of the belt-type continuously variable transmission and a friction engagement device, and the shift control valve includes: Including a sheave shift control valve that controls a sheave hydraulic pressure that sets an operating state of the movable sheave, and a clutch shift control valve that controls a clutch hydraulic pressure that sets an operating state of the friction engagement device, and the hydraulic pressure holding mechanism includes: A sheave hydraulic pressure holding mechanism that holds the hydraulic pressure supplied from the auxiliary oil pump and acting on the movable sheave; and a clutch hydraulic pressure holding mechanism that holds the hydraulic pressure supplied from the auxiliary oil pump and acting on the friction engagement device. And adjusting the hydraulic pressure supplied from the auxiliary oil pump to the movable sheave to a predetermined set hydraulic pressure, and the discharge pressure of the auxiliary oil pump exceeds the set hydraulic pressure Wherein the case is a hydraulic control device for an automatic transmission characterized in that it further comprises a pressure regulating mechanism for communicating between the sub-opening and said frictional engagement device.

According to a sixth aspect of the present invention, in the fifth aspect of the present invention, the hydraulic pressure holding mechanism is provided between the main discharge port and the sheave shift control valve, and the main discharge port to the sheave shift control valve. A first sheave check valve that allows the flow of oil only in the direction of the oil, and oil provided only between the main discharge port and the clutch speed change control valve provided between the main discharge port and the clutch speed change control valve. A first clutch check valve that allows the flow of oil, and a second sheave that is provided between the sub-discharge port and the movable sheave and that allows oil to flow only in the direction from the sub-discharge port to the hydraulic operating portion. A check valve, and a second clutch check valve that is provided between the sub discharge port and the friction engagement device and allows oil to flow only in the direction from the sub discharge port to the friction engagement device. It is characterized by A hydraulic control system for an automatic transmission.

The invention according to claim 7 is the invention according to claim 5 , wherein the pressure regulating mechanism opens the drain port when the discharge pressure of the auxiliary oil pump exceeds the set hydraulic pressure, and passes through the drain port. The hydraulic control device for an automatic transmission includes a relief valve that allows the auxiliary discharge port and the friction engagement device to communicate with each other.

According to an eighth aspect of the present invention, in the fifth aspect of the present invention, the pressure adjusting mechanism is provided between the sub discharge port and the hydraulic operation unit, and is directed from the hydraulic operation unit to the sub discharge port. And a check valve that opens the valve when the discharge pressure of the auxiliary oil pump exceeds the set hydraulic pressure and causes the auxiliary discharge port and the friction engagement device to communicate with each other. Is a hydraulic control device for an automatic transmission.

On the other hand, the invention according to claim 9 is the invention according to claim 1 or 2 , wherein the shift control valve opens when a predetermined control oil pressure is applied to the control port, and communicates between the input port and the output port. And a normally closed switching valve that shuts off the input port and opens the drain port when the control hydraulic pressure does not act on the control port, and closes the drain port. When the source of the hydraulic pressure supplied to the hydraulic operating unit is switched from the main oil pump to the sub oil pump, the automatic discharge pump is configured to cause the discharge pressure of the sub oil pump to act as the control oil pressure on the control port. This is a hydraulic control device for a transmission.

The invention of claim 10 is the invention of claim 9 , wherein the larger one of the discharge pressure of the main oil pump or the hydraulic pressure based thereon and the discharge pressure of the sub oil pump is selected as the maximum select pressure, A hydraulic control device for an automatic transmission, wherein the maximum select pressure or a hydraulic pressure based thereon is applied to the control port as the control hydraulic pressure.

According to an eleventh aspect of the present invention, in the first or second aspect of the present invention, the shift control valve is configured such that the discharge pressure of the main oil pump or a hydraulic pressure based thereon acts as the first control hydraulic pressure on the first control port. When the first input port and the first output port communicate with each other and the first drain port is closed, and the first control hydraulic pressure does not act on the first control port, the first input port and the first output port are closed. A normally closed first switching valve that shuts off from one output port and opens the first drain port, and the discharge pressure of the auxiliary oil pump acts as a second control oil pressure on the second control port In addition, when the second input port and the second output port communicate with each other and the second drain port is closed, and the second control hydraulic pressure does not act on the second control port, A second switching valve having a normally closed characteristic that communicates between the two output ports and the drain port and closes the second input port; and the second control port, the second input port, and the auxiliary discharge port Are connected to each other, and the second output port and the first drain port are in communication with each other, and the generation source of the hydraulic pressure supplied to the hydraulic operation unit is switched from the main oil pump to the sub oil pump. A hydraulic control device for an automatic transmission, wherein the sub-discharge port and the hydraulic operation unit are directly communicated with each other via the first drain port.

The invention according to claim 12 is the invention according to claim 1 or 2 , wherein the speed change control valve is based on a discharge pressure of the main oil pump or a control pressure and a pressure regulating port in which the action directions of oil pressures oppose each other. When the hydraulic pressure acts as the control hydraulic pressure, the input port and the output port are communicated and the drain port is closed according to the magnitude relationship of the control hydraulic pressure acting on the control port and the pressure regulating port, respectively. When switching between the state and the state between the input port and the output port and the state where the drain port is opened, and when the control oil pressure does not act on either the control port or the pressure regulating port, to include switching Kawaben configured to so that closing the communicating and the drain port between said output port and said input port A hydraulic control device for an automatic transmission according to symptoms.

According to a thirteenth aspect of the present invention, in the twelfth aspect of the present invention, the switching valve is configured such that the control port, the pressure adjusting port, and the main discharge port communicate with each other, and the input port and the main discharge port are connected to each other. A feedback port that communicates via a first check valve that allows the flow of oil only in the direction from the main discharge port to the input port, and that applies hydraulic pressure opposite to the pressing direction of the output port and the control port; The hydraulic operation part and the sub discharge port communicate with each other via a second check valve that allows oil flow only in the direction from the sub discharge port to the output port, the feedback port, and the hydraulic operation unit. And an urging member for applying a load in the same direction as the direction of hydraulic pressure of the control port. A hydraulic control device.

  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 a gear ratio for restarting. The hydraulic pressure generated by the oil pump is directly supplied to the hydraulic operating unit, and the hydraulic pressure supplied to the hydraulic operating unit is held by the hydraulic holding mechanism. In other words, when the hydraulic pressure generated by the sub oil pump is supplied to the hydraulic operating unit instead of the main oil pump, the hydraulic pressure is supplied only to the limited hydraulic circuit portion where the hydraulic pressure is held by the hydraulic holding mechanism. Is done. After the desired hydraulic pressure is supplied to the hydraulic operating unit, the hydraulic pressure is held by the hydraulic pressure holding mechanism. In addition, since the part where the hydraulic pressure acts is limited to the hydraulic operating part and a part of the hydraulic circuit around it, the oil leakage that occurs in the circuit compared to the case where the hydraulic pressure is supplied to the hydraulic circuit of the entire device. The location and quantity of the will also decrease. Therefore, when the main power source is stopped, the discharge ratio to be generated by the secondary oil pump is small in order to set the gear ratio for restarting with the automatic transmission, and therefore, the low pump capacity as the secondary oil pump. Can be used. 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 first aspect of the present invention, the hydraulic pressure generated by the auxiliary oil pump is supplied to the automatic transmission from the state where the hydraulic pressure control of the automatic transmission is executed by the hydraulic pressure generated by the main oil pump. First, the operation of the auxiliary power source is started, and the discharge pressure of the auxiliary oil pump that is started to be driven by the auxiliary power source is set in advance as, for example, the minimum required oil pressure in the hydraulic operating part of the automatic transmission. The operation of the main power source is stopped after waiting for the lower limit oil pressure to rise. Therefore, it is possible to reliably and smoothly switch the generation source of the hydraulic pressure from the main oil pump to the sub oil pump when the main power source is stopped.

According to the invention of claim 2, the hydraulic pressure holding mechanism that holds the hydraulic pressure supplied from the sub oil pump can be easily configured by using the check valve that regulates the flow direction of the oil in one direction. .

According to the invention of claim 3, the discharge pressure of the sub oil pump is adjusted to a predetermined set oil pressure by the pressure adjusting mechanism, and the hydraulic pressure is maintained in the hydraulic circuit in which the hydraulic pressure is held by the hydraulic operating portion and the hydraulic pressure holding mechanism. Supplied. Therefore, it is possible to easily adjust the hydraulic pressure supplied to the hydraulic operating unit to a desired set hydraulic pressure.

According to a fourth aspect of the present invention, the relief valve that opens and discharges the pressure when the oil pressure acting on the feedback port is higher than a predetermined set oil pressure is supplied from the sub oil pump to the hydraulic operating portion. A pressure regulating mechanism that regulates the hydraulic pressure to a predetermined set hydraulic pressure can be easily configured.

According to the fifth aspect of the present invention, when the main power source stops and the main oil pump does not generate hydraulic pressure with respect to the movable sheave and the friction engagement device, which are the hydraulic operating parts of the belt type continuously variable transmission. First, the hydraulic pressure generated by the auxiliary oil pump is first supplied to the movable sheave. Then, when the hydraulic pressure from the secondary oil pump is applied to the movable sheave and the sheave hydraulic pressure holding mechanism and the discharge pressure of the secondary oil pump exceeds a predetermined set hydraulic pressure, the hydraulic pressure from the secondary oil pump is changed to the friction engagement device and Supplied to the clutch hydraulic pressure holding mechanism. Therefore, when the hydraulic pressure generated by the sub oil pump instead of the main oil pump is supplied to the movable sheave and the friction engagement device, the hydraulic pressure is limited by the sheave hydraulic holding mechanism and the clutch hydraulic holding mechanism. It is only necessary to supply hydraulic pressure to only the portion. In addition, since the portion where the hydraulic pressure acts is limited to only the movable sheave and the frictional engagement device and a part of the hydraulic circuit around the movable sheave and the friction engagement device, the hydraulic pressure is applied to the hydraulic circuit of the entire device. The location and amount of oil leakage that occurs in For this reason, when the main power source is stopped, in order to set the speed ratio for restarting with the belt-type continuously variable transmission, the discharge pressure that must be generated by the sub oil pump can be reduced. An oil pump having a low pump capacity can be used. 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. Further, when hydraulic pressure is supplied to the movable sheave and the friction engagement device, the hydraulic pressure is preferentially supplied to the movable sheave, so that it can be controlled on the safe side against the belt slip, and the belt type continuously variable transmission. Reliability can be improved.

According to the invention of claim 6, by using a check valve that regulates the oil flow direction in one direction, a sheave hydraulic pressure holding mechanism and a clutch hydraulic pressure holding mechanism for holding the hydraulic pressure supplied from the sub oil pump The hydraulic pressure holding mechanism in the hydraulic control device of the belt type continuously variable transmission can be easily configured.

According to the seventh aspect of the invention, the relief valve that opens and exhausts the pressure when the oil pressure acting on the feedback port is higher than a predetermined set oil pressure is used to apply the discharge pressure of the sub oil pump to the feedback port. By making the drain port communicate with the friction engagement device, the belt type continuously variable pressure is adjusted to a predetermined set oil pressure from the auxiliary oil pump to the hydraulic operation unit such as the movable sheave and the friction engagement device. The pressure regulating mechanism in the hydraulic control device for the transmission can be easily configured.

According to the eighth aspect of the present invention, the check valve is opened when the oil pressure acting on the input port is higher than a predetermined set oil pressure, and the input port and the output port are communicated. By applying the discharge pressure of the oil pump and communicating the output port with the frictional engagement device, the hydraulic pressure supplied from the secondary oil pump to the hydraulic operating part such as the movable sheave and the frictional engagement device is set to a predetermined set hydraulic pressure. Therefore, it is possible to easily configure the pressure adjusting mechanism in the hydraulic control device of the belt type continuously variable transmission that adjusts the pressure to the same level.

On the other hand, according to the invention of claim 9, the shift control valve can be constituted by a switching valve having a normally closed characteristic (normally closed type). By applying a normally closed switching valve to the speed change control valve, it is possible to improve control responsiveness and ease of control when controlling the hydraulic pressure applied to the hydraulic operating part at the time of speed change. In addition, oil leakage in the hydraulic circuit can be reduced, and the efficiency of the automatic transmission can be improved.

According to the invention of claim 10 , for example, based on the discharge pressure of the main oil pump or the discharge pressure thereof, using two check valves disposed so as to face each other in the flow direction or a so-called Max Select type switching valve. The larger one of the hydraulic pressure and the discharge pressure of the auxiliary oil pump can be selected to act on the control port of the shift control switching valve. Therefore, the configuration of the device can be simplified. Further, it is possible to easily switch the generation source of hydraulic pressure without performing special control, and it is possible to improve the accuracy of hydraulic control.

According to the invention of claim 11 , the hydraulic pressure holding mechanism can also serve as the hydraulic pressure circuit portion extending from the auxiliary oil pump to the hydraulic pressure operating portion via the second switching valve and the first switching valve. That is, for example, the hydraulic pressure holding mechanism can be configured without providing a dedicated configuration such as a check valve or another switching valve. Therefore, the configuration of the apparatus can be simplified and the reliability of the apparatus can be improved.

Then, according to the invention of claim 12, 13, it is possible to improve the control response and easy control in controlling the oil pressure to be applied to the hydraulic unit at the time of speed change. Further, oil leakage in the hydraulic circuit can be reduced, and as a result, the efficiency of the automatic transmission can be improved.

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 an example of a structure of the conventional hydraulic control apparatus. It is a flowchart for demonstrating an example of the control performed by the hydraulic control apparatus of this invention. It is a flowchart for demonstrating the other example of the control performed by the hydraulic control apparatus of this invention. It is a time chart which shows the change of the discharge pressure of a sub oil pump at the time of performing control shown by the flowchart of FIG. It is a flowchart for demonstrating the further another example of the control performed by the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the action state of the hydraulic pressure at the time of switching a hydraulic pressure generation source in the hydraulic control apparatus of this invention. It is a time chart which shows the change of the discharge pressure of a sub oil pump at the time of performing control shown by the flowchart of FIG. It is a flowchart for demonstrating an example of the control performed by the hydraulic control apparatus of this invention in the case of a garage shift. It is a schematic diagram for demonstrating 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 flowchart for demonstrating an example of the control performed 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 modification of the structure of 6th Example shown in FIG. 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 the comparative example with respect to 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 modification of the structure of 8th Example shown in FIG. It is a schematic diagram for demonstrating the structure of 9th Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the modification of the structure of 9th Example shown in FIG. It is a schematic diagram for demonstrating the structure of 10th Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the structure of 11th Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the structure of 12th Example in the hydraulic control apparatus of this invention. It is a schematic diagram for demonstrating the pressure regulation characteristic of the speed change control valve in the structure of 12th Example shown in FIG. 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 mounted on a vehicle and sets a predetermined shift stage by appropriately engaging and releasing a friction engagement device such as a friction clutch or a brake to change a torque transmission path. A stepped automatic transmission, 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, or A toroidal type (or traction) that continuously changes the gear ratio by sandwiching a power roller between a pair of disks arranged opposite to each other and displacing the torque transmission point between the power roller and each disk. This is intended for hydraulic control of automatic transmissions such as continuously variable transmissions. 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, the hydraulic control device for an automatic transmission targeted by the present invention is driven by the output of a main power source connected to the automatic transmission, which is a driving force source of a vehicle, as a hydraulic pressure generation source. A main oil pump that generates hydraulic pressure and a power source that is separate from the main power source, and is driven by the output of a sub power source that can be operated and controlled independently of the main power source. It has an oil pump. During normal operation, that is, when the main power source is in operation, the main oil pump generates hydraulic pressure. When the main power source stops, the auxiliary oil pump generates hydraulic pressure, and the main oil pump or The oil discharged from the sub oil pump is configured to be supplied to a hydraulic operation part of the automatic transmission and an oil supply part that requires oil for lubrication and cooling. Since the auxiliary power source can be operated independently of the main power source as described above, when the main oil pump is driven by the main power source to generate hydraulic pressure, the auxiliary power source generates the auxiliary power source. The oil pump can also be driven to generate hydraulic pressure with the main oil pump. A more detailed configuration of the hydraulic control device for an automatic transmission that is the subject of the present invention as described above will be described based on the following specific examples.

(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, and here, for example, an internal combustion engine such as a gasoline engine, a diesel engine, or an LPG engine is targeted. In the following description, the main power source 1, that is, the internal combustion engine 1 is referred to as an engine (ENG) 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 the transmission of the output torque of the engine 1 as a driving force source to generate hydraulic pressure, and obtains the 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. 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 automatically shifted through a check valve 5, a control valve 6, and the like. It communicates with the hydraulic operating part 7 of the machine.

  The oil supply unit 4 corresponds to the oil supply unit in the present invention. For example, the power of the engine 1 is transmitted during traveling of the vehicle, such as a gear transmission mechanism and a bearing (none of which are shown) in the automatic transmission. This is a part that needs to be cooled and lubricated with oil when the automatic transmission is driven. 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 be temporarily stopped to supply oil. is there.

  The check valve 5 is a so-called check valve (check valve) corresponding to the check valve in the present invention, and in the oil passage that connects the discharge port 2o of the mechanical oil pump 2 and the control valve 6, the discharge port 2o The oil flow from the control valve 6 side to the control valve 6 side is allowed, and conversely, the oil flow from the control valve 6 side to the discharge port 2o is stopped.

  The control valve 6 is a control valve constituted by a switching valve or the like for controlling the hydraulic pressure supplied to the hydraulic operating portion 7 during the shift control of the automatic transmission, that is, the shift hydraulic pressure in the present invention, and its input port 6i. Is communicated with the discharge side of the check valve 5, and the output port 6 o is communicated with the hydraulic actuator 7. Then, for example, the position of the spool is switched by a signal pressure supplied from a solenoid valve (not shown) or the like, and the hydraulic pressure supplied to the hydraulic operation unit 7 is appropriately controlled.

  On the other hand, the hydraulic operating unit 7 is, for example, a friction clutch and a friction brake that are operated in an engaged / released state when a predetermined gear is set in a stepped automatic transmission, and a vehicle driving force source and an automatic A frictional engagement device such as a friction clutch for transmitting / cutting power transmission to / from the transmission, or a movable sheave operated to change the groove width of the pulley of the belt type continuously variable transmission, or toroidal type This is a part where the engagement / release state and the operating state are controlled using hydraulic pressure when performing shift control of an automatic transmission, such as a hydraulic actuator operated to change the posture of the power roller of a continuously variable transmission .

  Therefore, the hydraulic operating section 7 corresponds to the hydraulic operating section in the present invention, and the control valve 6 that controls the shift hydraulic pressure applied to the hydraulic operating section 7 corresponds to the shift control valve of the present invention. doing. The discharge port 2o, which is driven by the output of the engine 1 to generate hydraulic pressure and discharges oil by the hydraulic pressure, communicates with the oil supply unit 4, and the discharge port 2o communicates with the hydraulic operation unit 7 via the control valve 6. The communicating mechanical oil pump 2 corresponds to the main oil pump in the present invention, and the discharge port 2o corresponds to the main discharge port in the present invention.

  An automatic transmission mounted on a vehicle needs to set a gear stage or a gear ratio at which the vehicle can be started in preparation for a subsequent restart when the vehicle is stopped. For this reason, even when the vehicle is stopped, it is necessary to keep the hydraulic pressure required to set a predetermined gear position (speed ratio) for re-starting on the hydraulic operating unit 7. In other words, the hydraulic operation unit 7 is capable of stopping 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 when the vehicle stops temporarily, 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. Therefore, conventionally, as shown in FIG. 2, for example, an electric oil pump 101 that is driven by an electric motor 100 to generate hydraulic pressure is provided in parallel with a mechanical oil pump 2 that is driven by the engine 1, and the engine 1 is stopped. Thus, when the mechanical oil pump 2 does not generate hydraulic pressure, the electric oil pump 101 generates hydraulic pressure and supplies the oil to the oil supply unit 4 and the hydraulic operation unit 7.

  However, in the conventional configuration as shown in FIG. 2, when the hydraulic pressure is generated by the electric oil pump 101 instead of the mechanical oil pump 2 when the engine 1 is stopped, the discharge pressure equivalent to that of the mechanical oil pump 2 is obtained. Alternatively, the electric oil pump 101 needs to generate a hydraulic pressure as a discharge amount. Therefore, an electric oil pump 101 having a relatively large capacity and physique must be used, which has been a limiting factor in promoting downsizing, weight reduction, and cost reduction of the apparatus.

  Therefore, in the hydraulic control device HCU according to the present invention, as described above, the oil supply unit 4 can temporarily stop the supply of oil when the stopped engine 1 is stopped. When the 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 7 at the minimum, or the speed ratio at the time of restart is maintained. In view of this, it is possible to reduce the size and weight of the oil pump provided separately from the mechanical oil pump 2 or to reduce the cost, focusing on the fact that the hydraulic pressure necessary for this purpose may be maintained.

  That is, as shown in FIG. 1, an electric motor 8 corresponding to the auxiliary power source in the present invention is provided as a power source that can be operated independently with respect to the engine 1, and on the output side of the electric motor 8, A rotor shaft (or input shaft) 9a of the electric oil pump 9 is connected.

  The electric oil pump 9 is driven by transmission of the output torque of the electric motor 8 as a driving force source to generate hydraulic pressure, and obtains the output torque of the electric motor 8 to drive the rotor shaft 9a. Thus, the oil is sucked from the suction port 9i, and the sucked oil is discharged from the discharge port 9o. As the pump mechanism of the electric oil pump 9, as with the mechanical oil pump 2, the rotary pump such as a gear pump, a trochoid pump, a vane pump, and a screw pump, or various configurations such as a piston pump are known. The pump can be adopted. The electric oil pump 9 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 9o.

  The discharge port 9o of the electric oil pump 9 is not communicated with the oil supply unit 4, but is directly communicated with the hydraulic operation unit 7 of the automatic transmission through only the check valve 10. An oil pressure sensor 11 for detecting the discharge pressure of oil discharged from the discharge port 9o, that is, the pressure detection means in the present invention is provided in the immediate vicinity of the discharge port 9o.

  Therefore, the electric oil pump 9 that is driven by the output of the electric motor 8 to generate hydraulic pressure and discharges oil by the hydraulic pressure directly communicates with the hydraulic operating portion 7 is the auxiliary oil pump in the present invention. The discharge port 9o corresponds to the sub discharge port in the present invention.

  Like the check valve 5 described above, the check valve 10 corresponds to the check valve in the present invention, and is an oil that communicates the discharge port 9o of the electric oil pump 9, the control valve 6 and the hydraulic operating portion 7. On the road, the flow of oil from the discharge port 9o to the control valve 6 and the hydraulic operation unit 7 side is allowed, and conversely, the flow of oil from the control valve 6 and the hydraulic operation unit 7 side to the discharge port 9o is blocked. It has become.

  An electronic control unit (ECU) 12 for electrically controlling the solenoid valve or the electric motor 8 in the hydraulic control unit HCU is provided. This electronic control unit 12 is mainly composed of a microcomputer as an example, and performs calculation according to a predetermined program based on input data and data stored in advance, and the operation state of the solenoid valve or the electric motor 8 is determined. It is configured to perform control. Further, for the electronic control unit 12, the above-described hydraulic pressure sensor 11, an oil temperature sensor (not shown) for detecting the temperature of oil, or a rotation speed sensor (not shown) for detecting the rotation speed of each rotating member. ) And the like are input.

  When hydraulic pressure is supplied from the electric oil pump 9 to the hydraulic actuator 7 by configuring the hydraulic circuit (or oil passage) that supplies hydraulic pressure from the electric oil pump 9 to the hydraulic actuator 7 as described above. In addition, it is possible to maintain the hydraulic pressure that acts on the hydraulic operating portion 7.

  That is, when the engine 1 is stopped, that is, when the mechanical oil pump 2 is not generating hydraulic pressure, when the electric oil pump 9 generates hydraulic pressure and discharges oil from the discharge port 9o, the oil passes through the check valve 10. Then, the fluid flows through the oil passages communicating with the hydraulic operation unit 7 and the control valve 6, respectively, and is supplied to the hydraulic operation unit 7 and the control valve 6. Among them, the oil supplied to the control valve 6 side is prevented from flowing by the check valve 5 (to the oil passage on the left side of the check valve 5 in FIG. 1). On the other hand, the oil supplied to the hydraulic operating unit 7 causes the hydraulic operating unit 7 to apply hydraulic pressure. Since the oil that has once passed through the check valve 10 is stopped by the check valve 10 in the direction of returning to the discharge port 9o, the oil pressure of the portion partitioned by the check valves 5, 10 and the hydraulic operation unit 7 is Eventually, the discharge pressure of the electric oil pump 9 is maintained.

  As described above, when hydraulic pressure is supplied from the electric oil pump 9 to the hydraulic operating unit 7 by the portion partitioned by the check valves 5 and 10 and the hydraulic operating unit 7, the hydraulic operating unit 7 is acted on. The hydraulic pressure holding mechanism in the present invention for holding the hydraulic pressure is configured.

  Therefore, for example, by controlling the discharge pressure of the electric oil pump 9 or adjusting the drain pressure of the control valve 6, the check valves 5 and 10 and the hydraulic operation section 7 are partitioned as described above. The hydraulic pressure of the portion is set to a shift hydraulic pressure that is applied to the hydraulic operating unit 7 in order to set a desired shift speed (speed ratio), and even when the engine 1 is stopped, a desired shift speed ( Transmission ratio) can be maintained.

  Further, when the oil is discharged by the electric oil pump 9 instead of the mechanical oil pump 2 as described above, the oil is divided by the check valves 5 and 10 and the hydraulic operation unit 7 as described above and limited. It is supplied only to the part that has been applied, and is not supplied to the oil supply unit 4 or the like as in normal times. For this reason, the pump capacity required for the hydraulic pressure generation source is reduced as compared with the case where oil is supplied to the entire apparatus as usual. In addition, since the range in which the hydraulic pressure acts is limited as compared with the case where oil is supplied to the entire apparatus, the number of locations where oil leakage or the like occurs is reduced, and the loss is reduced accordingly. That is, the efficiency of the apparatus is improved. For these reasons, a low capacity, small size, and light weight can be adopted as the electric oil pump 9. As a result, the entire apparatus can be reduced in size and weight, the efficiency of the automatic transmission can be improved, and the fuel consumption of the vehicle can also be improved.

  A control example of the hydraulic control unit HCU having the configuration shown in FIG. 1 as described above will be described. FIG. 3 is a flowchart for explaining an example of the control. The routine shown in this flowchart is repeatedly executed every predetermined short time. In addition, in the routine shown in the flowchart of FIG. 3, it is a precondition for starting control that there is a command to execute an eco-run for the vehicle.

  Therefore, when the eco-run start command is output (step S10), first, the operation of the electric oil pump 9 is started (step S20). That is, the operation control of the electric motor 8 is started and the electric oil pump 9 is driven.

  After the operation of the electric oil pump 9 is started, the operation of the engine 1 is stopped (step S30). When the eco-run release command is output (step S40), first, the operation of the stopped engine 1 is started (step S50). That is, the engine 1 is restarted.

  After the operation of the engine 1 is resumed, the operation of the electric oil pump 9 is stopped (step S60). Thereafter, this routine is once ended.

  An example of more detailed control based on the routine shown in the flowchart of FIG. 3 is shown in the flowcharts of FIGS. Among these, the routine shown in the flowchart of FIG. 4 is a detailed example of the control from step S20 to step S30 in the flowchart of FIG. That is, this is an example of control related to switching of the hydraulic pressure generation source from the mechanical oil pump 2 to the electric oil pump 9 when the engine 1 is stopped during the eco-run.

  In the flowchart of FIG. 4, when the operation of the electric oil pump 9 is started in step S20, the discharge pressure P of the electric oil pump 9 is measured (step S21). As described above, the discharge pressure P can be detected by the hydraulic pressure sensor 11 set in the immediate vicinity of the discharge port 9o of the electric oil pump 9. Then, it is determined whether or not the detected discharge pressure P is larger than the lower limit hydraulic pressure Ps (step S22). This lower limit hydraulic pressure Ps needs to be applied to the hydraulic operating section 7 in order to maintain the speed ratio setting required for re-starting in a state where the operation of the engine 1 during the eco-run is stopped. This is a threshold set in advance as the minimum hydraulic pressure.

  If the discharge pressure P is still less than or equal to the lower limit oil pressure Ps, and if a negative determination is made in step S22, the process returns to step S21 described above. On the other hand, when the discharge pressure P becomes larger than the lower limit oil pressure Ps, the process proceeds to step S30 and the operation of the engine 1 is stopped. That is, in the control in steps S21 and S22, when the operation of the engine 1 is stopped during the eco-run, as shown in the time chart of FIG. 5, the discharge of the electric oil pump 9 is performed after the eco-run start command is output. The engine 1 is stopped after waiting for the pressure P to increase to the lower limit oil pressure Ps. Therefore, it is possible to reliably and smoothly switch the oil pressure generation source from the mechanical oil pump 2 to the electric oil pump 9 when the engine 1 is stopped during the eco-run.

  Next, the routine shown in the flowchart of FIG. 6 is a detailed example of the control from step S40 to step S60 in the flowchart of FIG. That is, the control example relates to switching of the hydraulic pressure source from the electric oil pump 9 to the mechanical oil pump 2 when the engine 1 is restarted and the electric oil pump 9 is stopped at the end of the eco-run.

  In the flowchart of FIG. 6, when the eco-run release command is output in step S40, first, the discharge pressure P0 of the electric oil pump 9 is measured before the engine 1 is restarted, that is, in a state where the engine 1 is stopped. And stored (step S41). Thereafter, when the engine 1 is restarted in step S50, after the engine 1 is restarted, that is, the current discharge pressure P of the electric oil pump 9 is measured (step S51).

  Then, it is determined whether or not the detected discharge pressure P is larger than a value (P0 + ΔP) obtained by adding the predetermined value ΔP to the above-described discharge pressure P0 (step S52). This predetermined value ΔP is a hydraulic operating part for maintaining the setting of the gear ratio required at the time of restart when switching the hydraulic pressure source from the electric oil pump 9 to the mechanical oil pump 2 again at the end of the eco-run. 7 is a predetermined value set in advance as a margin so that the hydraulic pressure that needs to be applied to 7 does not decrease.

  If the discharge pressure P is still less than or equal to the value obtained by adding the predetermined value ΔP to the discharge pressure P0 (P0 + ΔP), if the determination in step S52 is negative, the process returns to step S51 described above. On the other hand, when the discharge pressure P becomes larger than the value (P0 + ΔP) obtained by adding the predetermined value ΔP to the discharge pressure P0, the process proceeds to step S60, and the operation of the electric oil pump 9 is stopped.

  As described above, this control relates to switching of the hydraulic pressure generation source when the eco-run is finished. As shown in FIG. 7, the engine 1 is stopped during the eco-run and generated by the electric oil pump 9. The hydraulic pressure generated by the mechanical oil pump 2 when the engine 1 is restarted when the eco-run is finished from the state where the hydraulic pressure is applied to the hydraulic operating portion 7 (FIG. 7A). This is control when switching to a state (FIG. 7B) in which hydraulic pressure is applied to and held by the hydraulic operating unit 7.

  As shown in FIG. 7B, when the engine 1 is restarted and hydraulic pressure is generated again by the mechanical oil pump 2, the discharge pressure of the mechanical oil pump 2 becomes the discharge pressure of the electric oil pump 9. As a result, the check valve 5 is opened and the oil from the mechanical oil pump 2 flows into the hydraulic actuator 7 side, and the check valve 10 is closed and the oil from the electric oil pump 9 to the hydraulic actuator 7 side is reached. Inflow is stopped. That is, when the engine 1 restarts and the discharge pressure of the mechanical oil pump 2 increases, when the discharge pressure of the mechanical oil pump 2 exceeds the discharge pressure of the electric oil pump 9, automatic Thus, the hydraulic pressure source is switched from the electric oil pump 9 to the mechanical oil pump 2. In this case, the discharge pressure of the electric oil pump 9 is opposed to the discharge pressure of the mechanical oil pump 2 before and after the check valve 10 and rises to the vicinity of the discharge pressure of the mechanical oil pump 2.

  If the operation of the electric oil pump 9 is stopped immediately after switching the hydraulic pressure source, the hydraulic pressure supplied to the hydraulic operating unit 7 may become unstable. A predetermined value ΔP is provided as a margin when it is determined that the operation of the electric oil pump 9 is stopped. Therefore, as shown in the time chart of FIG. 8, after the engine 1 is restarted, the electric oil pump 9 is stopped after the discharge pressure P of the electric oil pump 9 is increased by the predetermined value ΔP. The Therefore, the oil pressure source is switched from the electric oil pump 9 to the mechanical oil pump 2 reliably and smoothly when the engine 1 is restarted and the operation of the electric oil pump 9 is stopped at the end of the eco-run. be able to.

  In the control example shown in the flowchart of FIG. 9, the automatic transmission shifts frequently between the N (neutral) range and the D (drive) range, or between the N range and the R (reverse) range. This is an example of control suitable when a so-called garage shift is performed. That is, in the routine shown in the flowchart of FIG. 9, the precondition for starting control is that the garage shift as described above is performed.

  Therefore, for example, when a signal indicating that a garage shift is executed is output from a detection value of a sensor (not shown) that detects the position of the shift lever (step S71), first, the operation of the electric oil pump 9 is performed. Is started (step S72). When the garage shift is performed, the hydraulic operation unit 7, particularly an input clutch (not shown) for transmitting / disconnecting power from the engine 1 to the automatic transmission is frequently operated. Increased amount of oil. Therefore, there is a possibility that oil and hydraulic pressure will be insufficient only by discharge by the mechanical oil pump 2 at the normal time. Therefore, the control in step S72 is for solving the shortage of oil by operating the electric oil pump 9 together with the mechanical oil pump 2 when the garage shift is performed.

  When input clutch engagement control is started in the next step S73, the input side rotational speed Nt and the input clutch output side rotational speed Nout are measured (step S74). The rotational speeds Nt and Nout can be detected from, for example, rotational speed sensors (not shown) provided in each part of the automatic transmission.

  Then, it is determined whether or not the detected rotation speeds Nt and Nout are equal to each other (step S75). That is, here, the engagement state of the input clutch is confirmed and judged.

  If the rotational speeds Nt and Nout have not yet coincided and are determined negative in step S75, the process returns to step S74. On the other hand, if the respective rotational speeds Nt and Nout are equal and coincide with each other, that is, if the engagement of the input clutch is completed and it is determined affirmative in step S75, the process proceeds to step S76. The operation of the oil pump 9 is stopped. Thereafter, this routine is once ended.

  In this way, when the garage shift is performed and there is a possibility that the hydraulic pressure of the hydraulic operation unit 7 is insufficient, the electric oil pump 9 can be driven to compensate for the hydraulic shortage. Therefore, since hydraulic assistance by the electric oil pump 9 can be expected, a mechanical oil pump 2 having a low pump capacity can be employed. As a result, the entire apparatus can be reduced in size and weight, and as a result, the fuel consumption of the vehicle can be improved.

(Second embodiment)
FIG. 10 shows a part of a hydraulic circuit in a second embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. The example shown in FIG. 10 is an example of a configuration in which the hydraulic control device HCU according to the present invention is applied to a belt-type continuously variable transmission. The configuration of each part 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 hydraulic pressure sensor 11, the electronic control apparatus 12, etc. is also abbreviate | omitted.

  In the case of a belt-type continuously variable transmission, the hydraulic actuating section 7 that is operated at the time of shifting includes friction such as a movable sheave 7s that constitutes a mechanism for changing the groove width of the pulley, and an input clutch that transmits and shuts off the power of the engine 1. An engagement device 7c is provided. Thus, even when the hydraulic operation unit 7 is divided into a plurality of parts, as in the configuration shown in FIG. 10, for example, the hydraulic circuit for the movable sheave 7s is replaced with the hydraulic circuit having the configuration shown in FIG. The sheave check valves 5s, 10s and the sheave control valve 6s corresponding to the check valves 5, 10 and the control valve 6 are provided, and the clutch check valves 5c, 10c and the clutch control are provided in the hydraulic circuit for the friction engagement device 7c. By providing the valve 6c, it is possible to obtain a hydraulic control unit HCU that exhibits the same operations and effects as those of the first embodiment.

(Third embodiment)
FIG. 11 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. 11, a pressure adjusting mechanism for setting a hydraulic pressure acting on the hydraulic operating portion 7 to a predetermined set hydraulic pressure is provided in a hydraulic pressure supply circuit (oil passage) from the electric oil pump 9 to the hydraulic operating portion 7. It is an example of the provided structure.

  That is, in FIG. 11, the relief valve corresponding to the pressure regulating mechanism of the present invention is branched from the middle of the oil passage that connects the discharge port 9o of the electric oil pump 9, the movable sheave 7s, and the friction engagement device 7c. 13 is provided. More specifically, the relief valve branches from the discharge port 9o, the sheave check valve 10s, and the clutch check valve 10c in the oil passage that communicates the discharge port 9o with the movable sheave 7s and the friction engagement device 7c. Thirteen input ports 13i are in communication. Further, an oil passage that communicates the branch point and the input port 13 i and a feedback port 13 f of the relief valve 13 are communicated.

  The relief valve 13 is configured to open and discharge when the discharge pressure of the electric oil pump 9 acting on the feedback port 13f is higher than the pressing force by the elastic force of the spring 13s. Therefore, the pressure regulating mechanism by the relief valve 13 is configured to regulate the discharge pressure of the electric oil pump 9 according to the elastic force of the spring 13s and set the set hydraulic pressure. The oil that is discharged when the relief valve 13 is opened can be used for lubrication and cooling of each part in the automatic transmission.

  Thus, by providing a pressure adjusting mechanism capable of setting the hydraulic pressure applied to the hydraulic operating section 7 to a predetermined set hydraulic pressure in the hydraulic pressure supply circuit from the electric oil pump 9 to the hydraulic operating section 7. Thus, the hydraulic pressure supplied to the hydraulic operating section 7 can be easily adjusted to a desired set hydraulic pressure, and the hydraulic pressure can be efficiently supplied to the hydraulic operating section 7. Further, for example, when the hydraulic pressure supplied to the hydraulic pressure operating unit 7 becomes abnormally high due to some failure, the relief valve 13 opens and exhausts pressure, so that a function as a fail safe can be provided.

  The electric oil pump 9 can generate a hydraulic pressure in place of the mechanical oil pump 2 when the engine 1 is stopped during the eco-run. In normal operation, that is, when the engine 1 is in operation. In addition, the electric oil pump 9 can be operated as an auxiliary to the mechanical oil pump 2. An example of control for the belt type continuously variable transmission in that case is shown in the flowchart of FIG.

  In the flowchart of FIG. 12, first, various data for grasping the current operation state of the hydraulic control unit HCU is read. For example, the rotational speed Nmp of the mechanical oil pump 2 and the oil temperature Tho are detected, and the volumetric efficiency ηv of the mechanical oil pump 2 in that state is detected from a map set in advance based on the rotational speed Nmp and the oil temperature Tho. The obtained values are read by the electronic control unit 12 (step S81).

  Based on the various data read in step S81, the oil discharge amount (discharge flow rate) Qmp of the mechanical oil pump 2 is calculated (step S82). In addition, the clutch supply amount Qc and the sheave as oil supply amounts respectively required for the friction engagement device 7c and the movable sheave 7s in order to set the speed ratio required for the belt type continuously variable transmission at that time. The supply amount Qs, the lubrication amount Qlub as the oil supply amount required in the oil supply unit 4, and the leak amount Qd are calculated as the amount of oil leakage that inevitably occurs in the hydraulic circuit (step S83). .

  Based on each oil amount calculated in step S83, a required oil amount Qneed is calculated as an oil discharge amount required for the entire hydraulic control unit HCU (step S84). For example, the required oil amount Qneed can be calculated as the sum of the clutch supply amount Qc, the sheave supply amount Qs, the lubrication amount Qlub, and the leakage amount Qd obtained in step S83.

  Then, the required oil amount Qneed obtained in the above steps is compared with the oil discharge amount (discharge flow rate) Qmp to determine whether the required oil amount Qneed is larger than the oil discharge amount Qmp (step S85). ). If the required oil amount Qneed is larger than the oil discharge amount (discharge flow rate) Qmp and if a positive determination is made in step S85, the process proceeds to step S86, and the electric oil pump 9 is operated. That is, when the oil discharge amount Qmp of the mechanical oil pump 2 is insufficient with respect to the required oil amount Qneed, the electric oil pump 9 is operated to compensate for the shortage. Thereafter, this routine is once terminated.

  On the other hand, if the required oil amount Qneed is equal to or less than the oil discharge amount (discharge flow rate) Qmp, and if a negative determination is made in step S85, the electric oil pump 9 with respect to the required oil amount Qneed. Since the oil discharge amount Qmp of the mechanical oil pump 2 is sufficient even if the engine oil pump 2 is not operated, the process proceeds to step S87, the electric oil pump 9 is deactivated, and then this routine is once ended.

  As described above, according to the configuration of the hydraulic control device HCU of the present invention, when the hydraulic oil is generated by the mechanical oil pump 2 by the output of the engine 1 at the normal time, the electric motor is used as an auxiliary to the mechanical oil pump 2. The oil pump 9 can be operated to compensate for the shortage of the oil discharge amount. Therefore, the pump capacity of the mechanical oil pump 2 can be reduced as compared with the conventional one. As a result, the physique of the mechanical oil pump 2 can be reduced in size and weight, and the overall apparatus can be reduced in size, weight, and cost.

(Fourth embodiment)
FIG. 13 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. In the example shown in FIG. 13, a pressure adjusting mechanism for setting a hydraulic pressure acting on the hydraulic operating portion 7 to a predetermined set hydraulic pressure is provided in a hydraulic pressure supply circuit (oil passage) from the electric oil pump 9 to the hydraulic operating portion 7. It is the other structural example provided.

  That is, in FIG. 13, a relief valve 14 corresponding to the pressure regulating mechanism in the present invention is provided in the middle of an oil passage that connects the discharge port 9 o of the electric oil pump 9 and the hydraulic operation unit 7. The relief valve 14 is configured such that the hydraulic pressure acting on the hydraulic pressure operating portion 7 acts on the feedback port 14f as a feedback pressure. In other words, the discharge port 9o communicates with the input port 14i of the relief valve 14 in parallel with the oil passages that respectively connect the discharge port 9o and the hydraulic operation unit 7 via the check valve 10, and the relief valve 14 An oil passage that communicates the feedback port 14f and the hydraulic operation unit 7 is formed.

  The relief valve 14 is configured to open and discharge when the feedback pressure acting on the feedback port 14 f, that is, the hydraulic pressure acting on the hydraulic operating portion 7 is higher than the pressing force due to the elastic force of the spring 14 s. . Therefore, the pressure adjusting mechanism by the relief valve 14 is configured to adjust the hydraulic pressure acting on the hydraulic operating portion 7 according to the elastic force of the spring 14s and set the set hydraulic pressure. The oil that is discharged when the relief valve 14 is opened can be used for lubrication and cooling of each part in the automatic transmission.

  Thus, by providing a pressure adjusting mechanism capable of setting the hydraulic pressure applied to the hydraulic operating section 7 to a predetermined set hydraulic pressure in the hydraulic pressure supply circuit from the electric oil pump 9 to the hydraulic operating section 7. Thus, the hydraulic pressure supplied to the hydraulic operating section 7 can be easily adjusted to a desired set hydraulic pressure, and the hydraulic pressure can be efficiently supplied to the hydraulic operating section 7.

  Further, as in the relief valve 14 in the fourth embodiment, the hydraulic pressure acting on the hydraulic operating portion 7 is guided to the feedback port 14f and used as a feedback pressure, so that the set hydraulic pressure for the hydraulic operating portion 7 is maintained. The flow rate of oil discharged from the oil pump 9 can be reduced as much as possible. Therefore, the pump capacity of the electric oil pump 9 can be reduced, and the physique of the electric oil pump 9 can be reduced in size and weight.

  Further, in a state where a desired set oil pressure is applied to the hydraulic operating portion 7, for example, a state where a desired engagement state is achieved by the friction engagement device, the set oil pressure is applied to the feedback port 14f of the relief valve 14. By doing so, the relief valve 14 is opened and discharged. Therefore, the electric oil pump 9 in that case is in a no-load state or a state in which only a slight load is applied, so that the power consumption when driving the electric motor 8 of the electric oil pump 9 is suppressed to save power. be able to.

(5th Example)
FIG. 14 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. In the example shown in FIG. 14, a pressure adjusting mechanism for setting a hydraulic pressure acting on the hydraulic operating portion 7 to a predetermined set hydraulic pressure is provided in a hydraulic pressure supply circuit (oil passage) from the electric oil pump 9 to the hydraulic operating portion 7. It is the further another structural example provided.

  That is, in FIG. 14, a relief valve 15 is provided that branches from the middle of an oil passage that connects the discharge port 9 o of the electric oil pump 9 and the hydraulic operation unit 7, and corresponds to the pressure adjusting mechanism in the present invention. . More specifically, the input port 15 i of the relief valve 15 is communicated with a branch from between the discharge port 9 o and the check valve 10 in the oil passage that communicates the discharge port 9 o and the hydraulic operation unit 7. Further, an oil passage communicating the branch point and the input port 15i and a feedback port 15f of the relief valve 15 are communicated.

  In the relief valve 15, as in the case of the relief valve 13 in the third embodiment, the discharge pressure of the electric oil pump 9 acting on the feedback port 15f is higher than the pressing force by the elastic force of the spring 15s. It is configured to open and exhaust pressure. Therefore, the pressure regulating mechanism by the relief valve 15 is configured to regulate the discharge pressure of the electric oil pump 9 according to the elastic force of the spring 15s and set the set hydraulic pressure. The oil that is discharged when the relief valve 15 is opened is supplied to a portion of the hydraulic operating unit 7 that requires lubrication and cooling.

  Thus, by providing a pressure adjusting mechanism capable of setting the hydraulic pressure applied to the hydraulic operating section 7 to a predetermined set hydraulic pressure in the hydraulic pressure supply circuit from the electric oil pump 9 to the hydraulic operating section 7. Thus, the hydraulic pressure supplied to the hydraulic operating section 7 can be easily adjusted to a desired set hydraulic pressure, and the hydraulic pressure can be efficiently supplied to the hydraulic operating section 7.

  Further, in the relief valve 15 in the fifth embodiment, oil discharged from the electric oil pump 9 in order to maintain the set hydraulic pressure for the hydraulic operating unit 7 by using the hydraulic pressure acting on the hydraulic operating unit 7 as a feedback pressure. Can be reduced as much as possible. Therefore, the pump capacity of the electric oil pump 9 can be reduced, and the physique of the electric oil pump 9 can be reduced in size and weight.

  Further, in a state where a desired set oil pressure is applied to the hydraulic operation unit 7, for example, a desired engagement state is achieved by the friction engagement device, the set oil pressure is applied to the feedback port 15f of the relief valve 15. As a result, the relief valve 15 is opened and discharged. Accordingly, in that case, the electric oil pump 9 is in a no-load state or a state in which only a slight load is applied, so that the power consumption when driving the electric motor 8 of the electric oil pump 9 is suppressed to save power. Can do. In a state where a desired set oil pressure is applied to the hydraulic operation unit 7, for example, in a state where a desired engagement state is achieved by the friction engagement device, the relief valve 15 is opened and discharged, and the discharged pressure is released. Oil is supplied to the necessary parts for lubrication and cooling in the hydraulic operation unit 7. Therefore, when the hydraulic operation unit 7 is operated, for example, when engaged with the friction engagement device, the oil for lubrication / cooling can be reliably supplied to a portion that requires lubrication / cooling, such as a friction material.

(Sixth embodiment)
FIG. 15 shows part of a hydraulic circuit in a sixth embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. In the example shown in FIG. 15, a pressure adjusting mechanism for setting a hydraulic pressure acting on the hydraulic operating unit 7 to a predetermined set hydraulic pressure is provided in a hydraulic pressure supply circuit (oil passage) from the electric oil pump 9 to the hydraulic operating unit 7. This is an example of a configuration provided for a belt type continuously variable transmission.

  That is, in FIG. 15, a relief valve 16 is provided which branches from the middle of an oil passage communicating the discharge port 9o of the electric oil pump 9 and the movable sheave 7s and corresponds to the pressure adjusting mechanism in the present invention. More specifically, the input port 16i of the relief valve 16 is communicated with a branch from between the discharge port 9o and the sheave check valve 10s in the oil passage communicating the discharge port 9o and the movable sheave 7s. Further, an oil passage communicating the branch point and the input port 16i and a feedback port 16f of the relief valve 16 are communicated. The output port (or drain port) 16o of the relief valve 16 and the friction engagement device 7c are communicated with each other.

  The relief valve 16 opens when the discharge pressure of the electric oil pump 9 acting on the feedback port 16f is higher than the pressing force by the elastic force of the spring 16s, and opens the input port 16i and the output port 16o. The discharge port 9o of the electric oil pump 9 and the friction engagement device 7c are communicated with each other.

  Therefore, the pressure regulating mechanism by the relief valve 16 is configured to regulate the hydraulic pressure discharged from the electric oil pump 9 and acting on the movable sheave 7s according to the elastic force of the spring 16s and set the set hydraulic pressure. Thus, after the hydraulic pressure acting on the movable sheave 7s is adjusted to the set hydraulic pressure, the relief valve 16 is opened, and the discharge port 9o of the electric oil pump 9 and the friction engagement device 7c are communicated. That is, the supply of hydraulic pressure to the friction engagement device 7c is started.

  Thus, by providing a pressure adjusting mechanism capable of setting the hydraulic pressure applied to the hydraulic operating section 7 to a predetermined set hydraulic pressure in the hydraulic pressure supply circuit from the electric oil pump 9 to the hydraulic operating section 7. Thus, the hydraulic pressure supplied to the hydraulic operating section 7 can be easily adjusted to a desired set hydraulic pressure, and the hydraulic pressure can be efficiently supplied to the hydraulic operating section 7.

  Further, as in the sixth embodiment, a circuit for supplying the discharge pressure of the electric oil pump 9 to the movable sheave 7s and the friction engagement device 7c using the relief valve 16 is configured, whereby the electric oil pump 9 In the case where the hydraulic pressure generated in step S3 is supplied to the movable sheave 7s and the friction engagement device 7c, first, the hydraulic pressure is supplied to the movable sheave 7s, and the set hydraulic pressure that acts on the movable sheave 7s is ensured. Hydraulic pressure is supplied to the friction engagement device 7c. That is, when hydraulic pressure is supplied to the movable sheave 7s and the friction engagement device 7c by the electric oil pump 9, the hydraulic pressure is preferentially supplied to the movable sheave 7s. Therefore, the shift control in the belt-type continuously variable transmission that operates the movable sheave 7s to change the groove width of the pulley can be executed on the safety side against the belt slip, and the reliability of the belt-type continuously variable transmission Can be improved.

  FIG. 16 shows a modification of the sixth embodiment, and shows a part of the hydraulic circuit in the modification. The example shown in FIG. 16 is an example in which the pressure regulating mechanism according to the present invention is configured by using a check valve 17 instead of the relief valve 16 having the configuration shown in FIG.

  That is, in FIG. 16, a check valve 17 is provided that branches off from the middle of an oil passage that connects the discharge port 9 o of the electric oil pump 9 and the movable sheave 7 s. More specifically, the input port 17i of the check valve 17 is communicated with a branch from between the discharge port 9o and the sheave check valve 10s in the oil passage communicating the discharge port 9o and the movable sheave 7s. The output port 17o of the check valve 17 and the friction engagement device 7c are communicated with each other.

  The check valve 17 is provided between the discharge port 9o of the electric oil pump 9 and the friction engagement device 7c as described above, and controls the flow of oil in the direction from the friction engagement device 7c to the discharge port 9o. This is a so-called backflow prevention valve (check valve) that restricts oil flow in the direction from the discharge port 9o to the friction engagement device 7c, and further acts in the direction from the discharge port 9o to the friction engagement device 7c. A spring 17s for generating a load in a direction opposite to the hydraulic pressure is provided. Therefore, it opens only when the discharge pressure of the electric oil pump 9 is higher than the pressing force due to the elastic force of the spring 17s, and the input port 17i and the output port 17o communicate with each other, that is, the discharge port of the electric oil pump 9 9o and the friction engagement device 7c are configured to communicate with each other.

  Also in the configuration of the modification shown in FIG. 16, the same operation and effect as in the case of the sixth embodiment can be obtained by appropriately adjusting the elastic force of the spring 17s.

(Seventh embodiment)
FIG. 17 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. In the example shown in FIG. 17, a normally closed switching valve that opens when a predetermined control hydraulic pressure is applied is used as a control valve 6 for controlling the transmission hydraulic pressure that sets the operating state of the hydraulic operation unit 7. It is an example of the structure used.

  The control valve 6 for controlling the shift hydraulic pressure for setting the operating state of the hydraulic operating portion 7, that is, the shift control valve in the present invention, is not required from the viewpoint of control response of the hydraulic control in the shift control and ease of control. It is preferable to apply one having a mary-close characteristic. However, if, for example, a normally closed select valve 200 as shown in FIG. 18 is used for the control valve 6 in the configuration of the first embodiment, the source of hydraulic pressure is supplied from the mechanical oil pump 2. When switching to the electric oil pump 9, when the hydraulic pressure PL generated by the mechanical oil pump 2 drops and the control oil pressure Psol for the normally close select valve 200 becomes 0, the select valve 200 is closed. At the same time, the drain port 200d is opened. In this state, when the hydraulic oil Pm is generated by the electric oil pump 9 and oil is discharged by the hydraulic oil Pm, a large amount of oil from the electric oil pump 9 may leak from the drain port 200d of the select valve 200. There is. Therefore, the hydraulic control unit HCU according to the present invention is configured as follows so that the hydraulic pressure source can be appropriately switched even when a normally closed characteristic is used for the shift control valve. Has been.

  That is, in FIG. 17, the control valve 6 corresponding to the shift control valve of the present invention is constituted by a select valve 18. This select valve 18 is a control valve having a so-called normally closed characteristic (normally closed type), and includes an input port 18i and an output port 18o, a control port 18c for applying a control oil pressure, and an action of the oil pressure of the control port 18c. A feedback port 18f that causes the discharge pressure of the output port 18o to act as a feedback pressure in a direction opposite to the direction, and a spring 18s that generates a load in a direction opposite to the direction in which the control port 18c acts on the hydraulic pressure.

  When a predetermined control oil pressure acts on the control port 18c, the input port 18i and the output port 18o communicate with each other, the drain port 18d is closed, and the control oil pressure does not act on the control port 18c. Is configured to block between the input port 18i and the output port 18o and open the drain port 18d.

  In addition, the discharge side of the check valve 5 is communicated with the input port 18i of the select valve 18, and the hydraulic operation unit 7 is communicated with the output port 18o. The control port 18c has a signal pressure Psol adjusted by the solenoid valve 20 or the like based on the discharge pressure of the mechanical oil pump 2 or the discharge pressure Pm of the electric oil pump 9 via a predetermined switching mechanism 19. Is input as control hydraulic pressure. The switching mechanism 19 is composed of, for example, a general switching valve, and selects either the input signal pressure Psol or the discharge pressure Pm and outputs it as a control hydraulic pressure to the control port 18c. Is configured to do.

The pressure receiving area of the control port 18c of the select valve 18 is Apm, the pressure receiving area of the feedback port 18f of the select valve 18 is Afb, the load of the spring 18s of the select valve 18 is W, and the discharge pressure of the electric oil pump 9 is Pm. Then, when the electric oil pump 9 is activated,
Apm> Afb + W / Pm
The shape dimension of each port 18c, 18f of the select valve 18 and the shape dimension / material or spring constant of the spring 18s are set so that the following relational expression is established.

  Thus, by setting the shape dimensions or spring constant of each part of the select valve 18 and configuring the hydraulic circuit provided with the select valve 18, the normally closed select valve 18 is used. A shift control valve can be configured. That is, when the hydraulic pressure source is switched from the mechanical oil pump 2 to the electric oil pump 9, the discharge pressure Pm of the electric oil pump 9 is increased as the electric oil pump 9 generates the hydraulic pressure. Since the control oil pressure acts on the control port 18c of the select valve 18, the select valve 18 is opened, the input port 18i and the output port 18o are communicated, and the drain port 18d is closed. Therefore, the drain port 18d of the select valve 18 is not opened when the hydraulic pressure generation source is switched. Therefore, oil leakage in the hydraulic circuit can be reduced, and the efficiency of the automatic transmission can be improved.

  Since the normally closed select valve 18 can be used as a shift control valve, the shift hydraulic pressure controlled by the select valve 18 and supplied to the hydraulic operation unit 7 during the shift control is compared with the control hydraulic pressure of the select valve 18. Therefore, the hydraulic control for the shift control can be facilitated, and the responsiveness of the hydraulic control can be improved.

(Eighth embodiment)
FIG. 19 shows a part of a hydraulic circuit in an eighth embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. In the example shown in FIG. 19, a normally closed switching valve that opens when a predetermined control oil pressure is applied is used as the control valve 6 for controlling the transmission oil pressure that sets the operating state of the oil pressure operating unit 7. It is the other structural example used.

  In other words, the select valve 18 in the eighth embodiment is configured such that the higher one of the modulation pressure Pmod using the discharge pressure PL of the mechanical oil pump 2 as the original pressure and the discharge pressure Pm of the electric oil pump 9 is the maximum. The signal pressure Psol selected as the select pressure and regulated by the solenoid valve 21 based on the maximum select pressure is input to the control port 18c as the control oil pressure.

  Specifically, in FIG. 19, the discharge port 2 o of the mechanical oil pump 2 and the control port 21 c of the solenoid valve 21 are communicated via a check valve 22. The check valve 22 is a so-called check valve (check valve), and in the oil passage that connects the discharge port 2o of the mechanical oil pump 2 and the control port 21c of the solenoid valve 21, the check port 22 is connected to the control port 21c. The oil flow to the side is allowed, and conversely, the oil flow from the control port 21c side to the discharge port 2o is stopped.

  Further, the discharge port 9 o of the electric oil pump 9 is communicated via the check valve 23 in the middle of the oil passage that communicates the check valve 22 and the solenoid valve 21. The check valve 23 has the same configuration as the check valve 22 described above, and in the oil passage that connects the discharge port 9o of the electric oil pump 9 and the control port 21c of the solenoid valve 21, the discharge port 9o to the control port 21c. The flow of oil to the side is allowed, and conversely, the flow of oil from the control port 21c side to the discharge port 9o is stopped.

  The output port 21o of the solenoid valve 21 and the control port 18c of the select valve 18 are in communication. That is, the signal pressure Psol adjusted by the solenoid valve 21 and output from the output port 21o is input to the control port 18c of the select valve 18 as the control hydraulic pressure.

That is, the check valves 22 and 23 are arranged so that the directions in which the oil flow is allowed to face each other, and when one of the check valves 22 and 23 is open, the other is always closed. It will be. In other words, partitioned by the check valve 22 and 23, also in the portion in communication with the solenoid valve 21 from therebetween, the check valve 22 towards the hydraulic high act (Moshiku check valve 23) only opens, The hydraulic pressure acts on the control port 21 c of the solenoid valve 21.

  Therefore, the higher one of the modulation pressure Pmod with the discharge pressure PL of the mechanical oil pump 2 as the original pressure and the discharge pressure Pm of the electric oil pump 9 is selected, and the selected hydraulic pressure is the present invention. The signal pressure Psol output from the discharge port 21o of the solenoid valve 21 acts on the control port 18c of the select valve 18 as the control oil pressure. ing.

The pressure receiving area of the control port 18c of the select valve 18 on which the signal pressure Psol from the solenoid valve 21 acts is Asol, the pressure receiving area of the feedback port 18f of the select valve 18 is Afb, the load of the spring 18s of the select valve 18 is W, If the discharge pressure of the electric oil pump 9 is Pm,
Asol> Afb + W / Pm
The shape dimension of each port 18c, 18f of the select valve 18 and the shape dimension / material or spring constant of the spring 18s are set so that the following relational expression is established.

  In this way, by setting the shape dimension or spring constant of each part of the select valve 18 and configuring the hydraulic circuit provided with the select valve 18, the configuration is normally similar to the above-described seventh embodiment. The shift control valve according to the present invention can be configured using the select valve 18 having the close characteristic. Therefore, it is possible to improve control responsiveness and ease of control when controlling the hydraulic pressure applied to the hydraulic operating unit 7 at the time of shifting. In addition, oil leakage in the hydraulic circuit can be reduced, and the efficiency of the automatic transmission can be improved.

  In the configuration of the eighth embodiment, the modulation pressure Pmod based on the discharge pressure PL of the mechanical oil pump 2 and the electric type using the two check valves 22 and 23 that are arranged to face each other in the flow direction. The larger one of the discharge pressure Pm of the oil pump 9 can be selected and applied to the control port 18c of the select valve 18 for shift control. Therefore, it is possible to easily switch the generation source of the hydraulic pressure without performing a special control, and it is possible to improve the accuracy of the hydraulic control. Further, since the switching mechanism 19 is not required as compared with the configuration of the seventh embodiment described above, the configuration of the apparatus can be simplified correspondingly.

  FIG. 20 is a modified example of the configuration of the eighth embodiment, and shows a part of the hydraulic circuit in the modified example. In the example shown in FIG. 20, the so-called max select type select valve 24 is used in place of the check valves 22 and 23 having the configuration shown in FIG. This is an example configured to act on the control port 18 c of the valve 18.

That is, in FIG. 20, the discharge port 2 o of the mechanical oil pump 2 and the discharge port 9 o of the electric oil pump 9 and the control port 21 c of the solenoid valve 21 are communicated via the select valve 24. Specifically, the discharge port 2o of the mechanical oil pump 2 and the input port 24a of the select valve 24 are in communication. Further, the discharge port 9o of the electric oil pump 9 and the input port 24b of the select valve 24 are communicated with each other. The output port 24o of the select valve 24 and the control port 21c of the solenoid valve 21 are communicated with each other. The select valve 24 is a so-called max-select type switching valve, and the higher one of the two input ports 24a and 24b provided with higher hydraulic pressure is selected, and the selected input port 24a ( Moshiku is configured so as to communicate the input port 24b) and the output port 24o.

  Therefore, the select valve 24 in the modified example shown in FIG. 20 has the same function as the two check valves 22 and 23 that are arranged opposite to each other in the flow direction in the configuration of the eighth embodiment shown in FIG. It can be replaced with these two check valves 22 and 23. Also in the configuration of the modified example shown in FIG. 20, the same operation and effect as in the case of the eighth embodiment shown in FIG. 19 can be obtained.

(Ninth embodiment)
FIG. 21 shows a part of a hydraulic circuit in a ninth embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. In the example shown in FIG. 21, a normally closed switching valve that opens when a predetermined control oil pressure is applied is used as the control valve 6 for controlling the transmission oil pressure that sets the operating state of the oil pressure operating unit 7. It is the further another structural example used.

  That is, the select valve 18 in the ninth embodiment includes the signal pressure Psol adjusted by the solenoid valve 25 based on the modulation pressure Pmod having the discharge pressure PL of the mechanical oil pump 2 as the original pressure, and the electric oil The larger one of the discharge pressure Pm of the pump 9 is selected as the maximum select pressure, and the maximum select pressure is input to the control port 18c as the control hydraulic pressure Pa.

  Specifically, in FIG. 21, the discharge port 2o of the mechanical oil pump 2 and the control port 25c of the solenoid valve 25 are communicated with each other. The output port 25o of the solenoid valve 25 and the control port 18c of the select valve 18 are communicated with each other via a check valve 26. The check valve 26 is a so-called check valve (check valve), and in the oil passage that connects the output port 25o of the solenoid valve 25 and the control port 18c of the select valve 18 to the control port 18c side. On the contrary, the oil flow from the control port 18c side to the output port 25o is stopped.

  Further, the discharge port 9 o of the electric oil pump 9 is communicated via a check valve 27 in the middle of an oil passage that communicates the check valve 25 and the select valve 18. The check valve 27 has the same configuration as the check valve 25 described above, and in the oil passage that connects the discharge port 9o of the electric oil pump 9 and the control port 18c of the select valve 18, the control port 18c is connected to the control port 18c. The oil flow to the side is allowed, and conversely, the oil flow from the control port 18c side to the discharge port 9o is stopped.

That is, the check valves 26 and 27 are arranged so that the directions allowing the oil flow are opposed to each other, and when one of the check valves 26 and 27 is open, the other is always closed. It will be. In other words, partitioned by the check valve 26 and 27, also in the portion in communication with the select valve 18 from therebetween, the check valve 26 towards the hydraulic high act (Moshiku is the check valve 27) only opens, The hydraulic pressure acts on the control port 18 c of the select valve 18.

  Therefore, either the signal pressure Psol adjusted by the solenoid valve 25 based on the modulated pressure Pmod whose original pressure is the discharge pressure PL of the mechanical oil pump 2 or the discharge pressure Pm of the electric oil pump 9 is larger. The selected hydraulic pressure, that is, the maximum select pressure in the present invention is applied to the control port 18c of the select valve 18 as the control hydraulic pressure Pa.

The pressure receiving area of the control port 18c of the select valve 18 on which the control hydraulic pressure Pa acts is Asol, the pressure receiving area of the feedback port 18f of the select valve 18 is Afb, the load of the spring 18s of the select valve 18 is W, and the electric oil pump 9 When the discharge pressure of Pm is Pm, when the electric oil pump 9 is operated,
Asol> Afb + W / Pm
The shape dimension of each port 18c, 18f of the select valve 18 and the shape dimension / material or spring constant of the spring 18s are set so that the following relational expression is established.

  In this way, by setting the shape dimensions or the spring constant of each part of the select valve 18 and configuring the hydraulic circuit provided with the select valve 18, the configuration is the same as in the seventh and eighth embodiments described above. The shift control valve according to the present invention can be configured by using the normally close select valve 18. Therefore, it is possible to improve control responsiveness and ease of control when controlling the hydraulic pressure applied to the hydraulic operating unit 7 at the time of shifting. In addition, oil leakage in the hydraulic circuit can be reduced, and the efficiency of the automatic transmission can be improved.

  In the configuration of the ninth embodiment, the flow direction is opposed to the output side of the solenoid valve 25 that regulates the modulation pressure Pmod based on the discharge pressure PL of the mechanical oil pump 2 and outputs the signal pressure Psol. Two arranged check valves 26, 27 are arranged, and using these two check valves 26, 27, the larger one of the signal pressure Psol and the discharge pressure Pm of the electric oil pump 9 is selected and used for shift control. It is possible to act on the control port 18c of the select valve 18. Therefore, it is possible to easily switch the generation source of the hydraulic pressure without performing a special control, and it is possible to improve the accuracy of the hydraulic control.

  In the configuration of the ninth embodiment, since the configuration around the check valve where oil leakage is relatively large is provided on the output side of the solenoid valve 25, the configuration around the check valve is more than that on the output side. Compared to the configuration of the above-described eighth embodiment provided on the input side of the solenoid valve 21 having a high hydraulic pressure, the amount of oil leakage around the check valve is reduced. Therefore, oil leakage in the hydraulic circuit can be reduced by that amount, and the efficiency of the automatic transmission can be improved.

  FIG. 22 is a modified example of the configuration of the ninth embodiment, and shows a part of the hydraulic circuit in the modified example. In the example shown in FIG. 22, a so-called Max Select type switching valve is used in place of the check valves 26 and 27 having the configuration shown in FIG. This is an example configured to act on 18 control ports 18c.

That is, in FIG. 22, the output port 25 o of the solenoid valve 25, the discharge port 9 o of the electric oil pump 9, and the control port 18 c of the select valve 18 are communicated via the select valve 28. Specifically, the output port 25o of the solenoid valve 25 and the input port 28a of the select valve 28 are in communication. Further, the discharge port 9o of the electric oil pump 9 and the input port 28b of the select valve 28 are communicated with each other. The output port 28o of the select valve 28 and the control port 18c of the select valve 18 are communicated with each other. The select valve 28 is a so-called Max Select type switching valve, and the higher one of the two input ports 28a, 28b that are provided is selected, and the input port 28a ( Moshiku is configured so as to communicate the input port 28b) and the output port 28o.

  Therefore, the select valve 28 in the modified example shown in FIG. 22 has the same function as the two check valves 26 and 27 that are arranged to face each other in the flow direction in the configuration of the ninth embodiment shown in FIG. It can be replaced with these two check valves 26 and 27. Also in the configuration of the modified example shown in FIG. 22, the same operation and effect as in the case of the ninth embodiment shown in FIG. 21 can be obtained.

(Tenth embodiment)
FIG. 23 shows part of a hydraulic circuit in a tenth embodiment of the hydraulic control unit HCU for an automatic transmission according to the present invention. In the example shown in FIG. 23, a normally closed switching valve that opens when a predetermined control hydraulic pressure is applied is used as a control valve 6 for controlling the shift hydraulic pressure that sets the operating state of the hydraulic operating section 7. This is an example of the configuration used, in which the check valves 5 and 10 constituting the hydraulic pressure holding mechanism of the present invention in each of the above-described embodiments are omitted.

  That is, in FIG. 23, the input port 18 i of the select valve 18 in the tenth embodiment is communicated with the discharge port 2 o of the mechanical oil pump 2. In addition, the output port 18 o communicates with the hydraulic operation unit 7. Further, the discharge pressure of the output port 18o is applied to the feedback port 18f as a feedback pressure. Further, a signal pressure Psol is supplied to the control port 18c from, for example, a solenoid valve (not shown). The drain port 18d communicates with the discharge port 9o of the electric oil pump 9 through the select valve 29.

  More specifically, the input port 29 i of the select valve 29 is communicated with the discharge port 9 o of the electric oil pump 9. Further, the output port 29o communicates with the drain port 18d of the select valve 18. The select valve 29 is adapted to receive the discharge pressure Pm of the electric oil pump 9 on the control port 29c. Further, the select valve 29 further generates a load in a direction opposite to the direction of the hydraulic pressure applied to the control port 29c. 29s is provided.

  The select valve 29 communicates between the input port 29i and the output port 29o and closes the drain port 29d, and blocks between the input port 29i and the output port 29o and opens the drain port 29d. It is comprised so that it can be switched to the state.

  That is, the select valve 29 communicates between the input port 29i and the output port 29o when the electric oil pump 9 generates hydraulic pressure and the discharge pressure Pm acts as a control pressure on the control port 29c. When the drain port 29d is closed, and the discharge pressure Pm does not act on the control port 29c, the input port 29i and the output port 29o are blocked and the drain port 29d is opened. Is configured to set.

  Therefore, when the hydraulic pressure is generated by the electric oil pump 9 and the discharge pressure Pm acts on the control port 29c, the input port 29i and the output port 29o of the select valve 29 are communicated with each other so that the electric oil The discharge port 9o of the pump 9 and the drain port 18d of the select valve 18 are communicated with each other. Accordingly, the discharge port 9o of the electric oil pump 9 and the hydraulic operation part 7 can be directly communicated with each other through the drain port 18d of the select valve 18, and as a result, the discharge pressure Pm of the electric oil pump 9 is directly hydraulically operated. The unit 7 can be supplied.

More specifically, if the discharge pressure of the electric oil pump 9 is Pm, the pressure receiving area of the control port 29c of the select valve 29 on which the discharge pressure Pm acts is Ak, and the load of the spring 29s of the select valve 29 is Wk. When the electric oil pump 9 is activated,
Pm> Wk / Ak
By satisfying the following relational expression, the discharge port 9o of the electric oil pump 9 and the hydraulic operating part 7 can be connected regardless of the configuration of each part of the control valve 6, that is, the select valve 18 and the hydraulic pressure of each part in the hydraulic circuit. It will be in the state of being connected directly. The oil discharged from the electric oil pump 9 is reliably supplied to the hydraulic operation unit 7.

  As described above, in the configuration of the tenth embodiment, like the configurations of the seventh, eighth, and ninth embodiments described above, the normally closed select valve 18 is used to change the speed change control valve in the present invention. Can be configured. Therefore, it is possible to improve control responsiveness and ease of control when controlling the hydraulic pressure applied to the hydraulic operating unit 7 at the time of shifting. In addition, oil leakage in the hydraulic circuit can be reduced, and the efficiency of the automatic transmission can be improved.

  Further, in the configuration of the tenth embodiment, when the electric oil pump 9 is operated, the electric oil pump 9 discharges regardless of the configuration of each portion of the select valve 18 or the relationship between the hydraulic pressures of the respective portions in the hydraulic circuit. Since a circuit that can supply the oil to be directly supplied to the hydraulic operation unit 7 can be configured, the degree of freedom in setting the configuration of each part of the select valve 18 or selecting the select valve 18 can be expanded.

  In the configuration of the tenth embodiment, the hydraulic pressure acting on the hydraulic operating portion 7 is held in the hydraulic circuit portion from the electric oil pump 9 to the hydraulic operating portion 7 via the select valve 29 and the select valve 18. It can also serve as a hydraulic holding mechanism. That is, for example, the check valves 5 and 10 constituting the hydraulic pressure holding mechanism of the present invention in the configuration of each of the above-described embodiments can be omitted. Therefore, the configuration of the apparatus can be simplified and the reliability of the apparatus can be improved.

(Eleventh embodiment)
FIG. 24 shows a part of a hydraulic circuit in an eleventh embodiment of the hydraulic control unit HCU for the automatic transmission according to the present invention. The example shown in FIG. 24 is opened when a predetermined control oil pressure is applied as the control valve 6 for controlling the transmission oil pressure for setting the operation state of the hydraulic operation unit 7 as in the tenth embodiment. This is a configuration example using a normally-closed characteristic switching valve, and is another configuration example in which the check valves 5 and 10 that constitute the hydraulic pressure holding mechanism of the present invention in each of the above-described embodiments are omitted.

  24, in the eleventh embodiment, a select valve 30 having two control ports 30c and 30f and two drain ports 30d and 30e is provided in place of the select valve 29 in the tenth embodiment. The drain port 18 d of the select valve 18 is communicated with the discharge port 9 o of the electric oil pump 9 via the select valve 30.

  More specifically, the input port 30 i of the select valve 30 is communicated with the discharge port 9 o of the electric oil pump 9. In addition, the output port 30 o communicates with the drain port 18 d of the select valve 18. The select valve 30 is adapted so that the discharge pressure Pm of the electric oil pump 9 acts on the control port 30c, and further exerts a hydraulic pressure in a direction opposite to the hydraulic pressure acting direction of the control port 30c. A control port 30 f is communicated with the discharge port 2 o of the mechanical oil pump 2. The other drain port 30e is in communication with a portion that needs to be supplied with oil for cooling or lubrication, such as the oil supply unit 4 described above. Further, one drain port 30d communicates with, for example, the oil pan 3 and the like, and is discharged from the drain port 30d.

  The select valve 30 communicates between the input port 30i and the output port 30o and closes the drain ports 30d and 30e, and blocks between the input port 30i and the output port 30o. Each drain port 30d, 30e is configured to be switched to an open state.

  That is, the select valve 30 is a mechanical oil pump 2 in which the electric oil pump 9 generates hydraulic pressure, and the discharge pressure Pm acts as a control pressure on one control port 30c and acts on the other control port 30f. When the discharge pressure is greater than the discharge pressure PL, the input port 30i and the output port 30o communicate with each other, and the drain ports 30d and 30e are both closed. When the hydraulic pressure is generated and the discharge pressure PL is larger than the discharge pressure Pm of the electric oil pump 9 acting as the control pressure on the other control port 30f and acting on the one control port 30c, or one control port When the discharge pressure Pm does not act on 30c, the input port 30i is disconnected from the output port 30o, and the input port 30i and the drain are disconnected. Communicating between the over bets 30e, and has a configuration to set a state in which communication between the output port 30o and the drain port 30d.

  Therefore, if the discharge pressure Pm of the electric oil pump 9 acting on the control port 30c of the select valve 30 is larger than the discharge pressure PL of the mechanical oil pump 2 acting on the control port 30f of the select valve 30, the select valve By connecting the 30 input ports 30i and the output port 30o, the discharge port 9o of the electric oil pump 9 and the drain port 18d of the select valve 18 are connected. Accordingly, the discharge port 9o of the electric oil pump 9 and the hydraulic operation part 7 can be directly communicated with each other through the drain port 18d of the select valve 18, and as a result, the discharge pressure Pm of the electric oil pump 9 is directly hydraulically operated. The unit 7 can be supplied.

  On the other hand, if the discharge pressure Pm of the electric oil pump 9 acting on the control port 30c of the select valve 30 is smaller than the discharge pressure PL of the mechanical oil pump 2 acting on the control port 30f of the select valve 30, the select The input port 30i and the output port 30o of the valve 30 are blocked, the drain port 30d of the select valve 30 and the drain port 18d of the select valve 18 are communicated, and the drain port 30e of the select valve 30 and, for example, oil The supply unit 4 is communicated. Therefore, without discharging the discharge pressure Pm of the electric oil pump 9 unnecessarily, oil discharged from the electric oil pump 9 by the discharge pressure Pm is used for lubrication and cooling of the oil supply unit 4 and the like, for example. Oil can be supplied to the necessary parts.

  As described above, in the configuration of the eleventh embodiment, as in the configurations of the seventh, eighth, ninth, and tenth embodiments described above, the select valve 18 having a normally closed characteristic is used to change the speed in the present invention. A control valve can be configured. Therefore, it is possible to improve control responsiveness and ease of control when controlling the hydraulic pressure applied to the hydraulic operating unit 7 at the time of shifting. In addition, oil leakage in the hydraulic circuit can be reduced, and the efficiency of the automatic transmission can be improved.

  Further, in the configuration of the eleventh embodiment, in addition to the actions and effects obtained by the configuration of the tenth embodiment, when the hydraulic pressure is applied to the hydraulic operating portion 7 by the mechanical oil pump 2, The electric oil pump 9 can supply oil to the required oil parts such as the oil supply 4. That is, when the oil supply by the mechanical oil pump 2 is insufficient, the electric oil pump 9 can assist.

(Twelfth embodiment)
FIG. 25 shows part of a hydraulic circuit in a twelfth embodiment of the hydraulic control unit HCU for an automatic transmission according to the present invention. Example shown in FIG. 25, as a control valve 6 for controlling the shifting oil pressure for setting the operating state of the hydraulic unit 7, exchange switching is configured so that to open when a predetermined control hydraulic pressure is applied This is an example of a configuration using a valve, and is a configuration in which a control pressure using a discharge pressure of the mechanical oil pump 2 as a source pressure in the normal direction is applied in the same direction as the feedback pressure.

  As described above, the control valve 6 for controlling the shift hydraulic pressure for setting the operation state of the hydraulic operation unit 7, that is, the shift control valve in the present invention, includes control response of the hydraulic control in the shift control and ease of control. In view of the above, it is preferable to apply a normally closed characteristic. Therefore, for example, by configuring as in the seventh to ninth embodiments described above, the shift control valve in the present invention can be configured using the select valve 18 having the normally close characteristic, and the control response of the hydraulic control And ease of control can be improved. However, even in such a case, when the hydraulic pressure generation source of the hydraulic control unit HCU is switched from the mechanical oil pump 2 to the electric oil pump 9, the discharge pressure Pm of the electric oil pump 9 is predetermined. During a short period of time when the pressure is increased to more than the oil pressure, the select valve 18 is closed, that is, the drain port 18d is open, and oil leakage from the drain port 18d inevitably occurs. Therefore, the hydraulic control unit HCU of the present invention shown in the twelfth embodiment is configured as follows so that oil leakage that occurs when the hydraulic pressure generation source is switched can be reduced as much as possible.

That is, in FIG. 25, the control valve 6 corresponding to the speed change control valve of the present invention is constituted by the select valve 31. The selector valve 31 includes a input port 31i and output port 31o, and a control port 31c for applying a control pressure, the discharge pressure of the output port 31o in the direction opposite to the oil pressure of the working direction of the control port 31c as a feedback pressure And a feedback port 31f to be operated. The select valve 31 has a spring 31s that generates a load in the same direction as the hydraulic pressure acting direction of the control port 31c, and further, a mechanical oil pump in a direction opposite to the hydraulic pressure acting direction of the control port 31c. Another control port 31g for applying a modulation pressure Pmod based on the two discharge pressures PL is provided.

Further, when the pressure receiving area of the feedback port 31f of the select valve 31 is Afb, the load of the spring 31s of the select valve 31 is W, and the discharge pressure of the electric oil pump 9 is Pm,
Pm x Afb <W
The shape dimension of the feedback port 31f of the select valve 31, the shape dimension / material of the spring 31s, the spring constant, and the like are set so that

  Therefore, in the select valve 31, when the signal pressure Psol adjusted by the solenoid valve 20 acts on the control port 31c, and when the discharge pressure PL of the mechanical oil pump 2 decreases, the signal pressure Psol and the modulation pressure are reduced. When both the rate pressures Pmod are 0, the input port 31i and the output port 31o are communicated with each other and the drain port 31d is closed. Then, for example, when the discharge pressure Pm of the electric oil pump 9 rises to a set pressure or higher and a feedback pressure higher than a predetermined value acts on the feedback port 31f, the input port 31i is disconnected from the output port 31o. The drain port 31d is opened.

When the electric oil pump 9 operates as a hydraulic pressure generation source of the hydraulic control unit HCU and discharges oil, the pressure receiving area of the control port 31c of the select valve 31 is Asol, and the control port 31g of the select valve 31 is Is the pressure receiving area of the feedback valve 31f of the select valve 31, Afb, the load of the spring 31s of the select valve 31 is W, the discharge pressure of the electric oil pump 9 is Pm, the discharge pressure of the mechanical oil pump 2 ( (Or the line pressure) is P L, the signal pressure that is regulated by the solenoid valve 20 and input to the control port 31 c is P sol, and the clutch pressure that is retained by acting on the hydraulic operation unit 7 is P c. The pressure-regulating formula showing the pressure-regulating characteristics of the select valve 31 as the hydraulic control valve 6 supplied to the
Pc = (Asol / Afb) × Psol−W / Afb + Pmod × Amod / Afb (1)
Can be expressed as

The pressure regulation formula of the select valve 31 represented by the above formula (1) is represented by a straight line A (solid line) in the pressure regulation characteristic diagram as shown in FIG. Here, for example, the pressure regulation expression indicating the pressure regulation characteristic of the select valve 200 in the configuration of the comparative example shown in FIG.
Pc = (Asol / Afb) × Psol−W / Afb (2)
This can be expressed as a straight line B (dashed line) when shown on the pressure regulation characteristic diagram of FIG. In this way, by constructing a hydraulic circuit using the normally closed select valve 31 as in the twelfth embodiment, the pressure regulating section of the select valve 31 is made more original than the comparative example. Therefore, the controllability of the hydraulic control for the hydraulic operation unit 7 is improved.

Thus, in the configuration of this twelfth embodiment, it is possible to use the cell Rekutobarubu 31 constitutes a speed change control valve in the present invention. In this case, the pressure regulation characteristic of the select valve 31 is, for example, the relationship between the control pressure of the hydraulic control valve 6 (that is, the select valve 31) that is applied to the hydraulic operating unit 7 and the hydraulic pressure that is applied to the hydraulic operating unit 7. In the pressure regulation characteristic diagram based on this, it is possible to have a mode that rises from the vicinity of the origin, and therefore, control responsiveness and controllability when controlling the hydraulic pressure applied to the hydraulic operating section 7 at the time of shifting are further improved. be able to.

  In addition, it is possible to smoothly switch the hydraulic pressure generation source from the mechanical oil pump 2 to the electric oil pump 9, and to reduce oil leakage in the hydraulic circuit as much as possible. As a result, the electric oil pump 9 can be reduced in size and weight, and the efficiency of the automatic transmission can be improved.

  The present invention is not limited to the specific examples described above. For example, in the configuration of each of the above-described embodiments, the electric oil pump 9 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 with a pump 32 (so-called valve pump, solenoid pump, solenoid valve pump, etc.) configured to generate Briefly describing the configuration, in FIG. 27, the valve pump 32 includes a coil portion 32 c provided with an electromagnetic coil 33, check valves 34 and 35 that restrict oil flow in one direction, and oil A valve (pump) portion 32v including an oil chamber 36 and the like in which suction and discharge are performed, and a plunger 32p that reciprocates in the oil chamber 36 are configured.

  The check valve 34 allows the flow of oil from the suction port 32 i into the oil chamber 36 at the suction port 32 i of the valve pump 32, and conversely prevents the flow of oil from the oil chamber 36 to the outside of the suction port 32 i. It is configured to stop. The check valve 35 allows oil to flow from the oil chamber 36 to the outside of the discharge port 32o at the discharge port 32o of the valve pump 32. On the contrary, the oil from the discharge port 32o to the oil chamber 36 is allowed. It is the structure which stops the flow of. The plunger 32 p is configured to reciprocate within the oil chamber 36 by the action of electromagnetic force of the electromagnetic coil 33.

  By controlling the current supplied to the electromagnetic coil 33, the plunger 32p can be reciprocated at high speed in the oil chamber 36. Therefore, along with the reciprocating operation of the plunger 32p, the oil can be repeatedly sucked and discharged in the oil chamber 36, and the valve pump 32 can function as a reciprocating volume pump. Therefore, by applying such a valve pump 32 as a sub oil pump in the present invention, the configuration of the apparatus is compared with a case where an electric oil pump 9 provided with, for example, a brushless rotary motor as a power source is used. It can be further simplified and 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, ENG), 2 ... Mechanical oil pump (main oil pump), 2o ... Discharge port (main discharge port), 4 ... Oil supply part, 5,10 ... Check valve (check valve), 6 ... Control valve (transmission control valve), 7 ... Hydraulic actuator, 8 ... Electric motor (sub power source, M), 9 ... Electric oil pump (sub oil pump), 9o ... Discharge port (sub discharge port), 11 ... Hydraulic sensor (pressure detection means), 12 ... Electronic control unit (ECU), HCU ... Hydraulic control unit.

Claims (13)

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 and supplies a shift hydraulic pressure that sets an operating state of a hydraulic operation unit that is operated at the time of shifting ,
A shift control valve that is driven by the output of the main power source to generate hydraulic pressure, a main discharge port that discharges oil by the hydraulic pressure communicates with the oil supply unit, and the main discharge port controls the shift hydraulic pressure A main oil pump communicating with the hydraulic operating part via
A sub-oil pump that is driven by the output of a sub-power source that can be operated independently of the main power source to generate hydraulic pressure, and a sub-discharge port that discharges oil by the hydraulic pressure directly communicates with the hydraulic operating unit When,
A hydraulic pressure holding mechanism that holds the hydraulic pressure acting on the hydraulic pressure operation section when hydraulic pressure is supplied from the sub oil pump to the hydraulic pressure action section ;
E Bei a pressure detecting means for detecting a delivery pressure of the auxiliary oil pump,
When switching the generation source of the hydraulic pressure supplied to the hydraulic operating section from the main oil pump to the sub oil pump, the discharge pressure of the auxiliary oil pump is increased to a predetermined lower limit hydraulic pressure required by the hydraulic operating section. hydraulic control apparatus for an automatic transmission, wherein that you stop the operation of the main power source. The hydraulic pressure holding mechanism is provided between the main discharge port and the shift control valve, and allows a flow of oil only in a direction from the main discharge port to the shift control valve; claims is provided between the discharge port and the front SL hydraulic unit characterized that you and a second check valve that allows the flow of oil only in the direction of the previous SL hydraulic unit from the sub-opening Item 2. The hydraulic control device for an automatic transmission according to Item 1. Hydraulic pressure of the automatic transmission according to claim 1 or 2, characterized that you said that the hydraulic pressure supplied prior SL hydraulic unit from the sub oil pump further comprises a regulating pressure regulating pressure mechanism to a predetermined set pressure Control device. The pressure regulating mechanism, the automatic transmission according to claim 3 in which the discharge pressure of the previous SL sub Oirupon flop is characterized that you including relief valve pressure discharge by opening the drain port when exceeded the set pressure Hydraulic control device. The hydraulic operation unit includes a movable sheave and a friction engagement device that operate at the time of shifting of the belt-type continuously variable transmission,
The shift control valve includes a sheave shift control valve that controls a sheave hydraulic pressure that sets an operating state of the movable sheave, and a clutch shift control valve that controls a clutch hydraulic pressure that sets an operating state of the friction engagement device,
The hydraulic retention mechanism holds the sheave pressure holding mechanism for holding the hydraulic pressure applied is supplied from the previous SL sub Oirupon flop to the movable sheave, the hydraulic pressure applied to the friction engagement device is supplied from the secondary oil pump Including a clutch hydraulic pressure holding mechanism
The hydraulic pressure supplied from the secondary oil pump to the movable sheave is adjusted to a predetermined set hydraulic pressure, and when the discharge pressure of the secondary oil pump exceeds the set hydraulic pressure, the secondary discharge port, the friction engagement device, A pressure regulating mechanism for communicating between the two
Hydraulic control system for an automatic transmission according to claim 1, wherein the this. A first sheave check valve that is provided between the main discharge port and the sheave shift control valve and that allows oil to flow only in a direction from the main discharge port to the sheave shift control valve; A first clutch check valve provided between the main discharge port and the clutch shift control valve and allowing oil to flow only in a direction from the main discharge port to the clutch shift control valve; and the sub discharge port and the second sheave check valve that allows the flow of oil only in the direction from the sub-opening provided Previous SL hydraulic unit between the movable sheave, the secondary discharge port and the friction Kosugakarigo device automatic transmission according to claim 5, characterized that you from the sub-opening is provided and a second clutch check valve that allows the flow of oil only in the direction to the friction engagement device between the Hydraulic control device for the machine. The pressure regulating mechanism, the relief of the discharge pressure of sub oil pump communicating with the frictional engagement device before and SL sub-opening through the drain port by opening the drain port when exceeded the set pressure The hydraulic control device for an automatic transmission according to claim 5, further comprising a valve . The pressure regulating mechanism is configured to stop the flow from the hydraulic unit is provided in the direction of oil to the secondary discharge port between said secondary discharge port and the hydraulic unit, the discharge of the pre-Ki auxiliary oil pump hydraulic pressure of the automatic transmission according to claim 5, characterized in that it comprises a check valve pressure Ru communicates with said friction engagement device before and SL sub-opening to open when exceeds the set pressure Control device. Before SL shift control valve closes the communication with and the drain port between and opening an input port and an output port when the predetermined control hydraulic pressure to the control port acts, the control oil pressure is applied to the control port A normally closed switching valve that shuts off between the input port and the output port and opens the drain port,
When switching the hydraulic pressure source for supplying the oil pressure operation unit from the main oil pump to the secondary oil pump, to apply a discharge pressure before Symbol auxiliary oil pump as the control pressure to the control port
Hydraulic control system for an automatic transmission according to claim 1 or 2, characterized and this. A hydraulic-based discharge pressure or that before Kinushi Oirupon flop selects whichever is greater with the previous SL discharge pressure of the sub Oirupon flop as Max select pressure, before the Max Select pressure or hydraulic based on it as the control oil pressure hydraulic control system for an automatic transmission according to claim 9, characterized in that to act on the serial control port. The shift control valve, when the discharge pressure or oil pressure based thereon before Kinushi oil pump to the first control port acts as the first control hydraulic pressure, communicating between the first input port and the first output port When the first drain port is closed and the first control hydraulic pressure does not act on the first control port, the first input port and the first output port are blocked and the first drain port is closed. Including a first switching valve with normally closed characteristics that opens;
When the discharge pressure of the auxiliary oil pump acts as a second control oil pressure on the second control port, the second input port communicates with the second output port, the second drain port is closed, and the second A second switching valve having a normally close characteristic that communicates between the second output port and the drain port and closes the second input port when the second control hydraulic pressure does not act on the control port;
The second control port and the second input port communicate with the sub-discharge port, and the second output port communicates with the first drain port;
When switching the hydraulic pressure source supplies the hydraulic unit from the main oil pump Previous Symbol sub Oirupon flop, thereby directly communicated with said hydraulic unit and said sub-opening through the first drain port The hydraulic control device for an automatic transmission according to claim 1 or 2 . The shift control valve, when the hydraulic pressure based on that the discharge pressure or the previous Kinushi oil pump to the control port and the pressure regulating port hydraulic working directions opposed to each other respectively act as a control pressure, the control port and the tone in response to the control oil pressure of the magnitude relationship acting respectively pressure port blocking, the state communicating and Doreen port between the close of the input and output ports, between said input port and said output port with switched between opened the life-and-death said drain port, if the previous SL control port and the control hydraulic pressure to either of the pressure regulating port does not act, communicating between said output port and said input port and hydraulic control system for an automatic transmission according to claim 1 or 2, characterized in a whatever child the configured switching Kawaben to close the drain port. The SWITCHING valve communicates with the control port and the pressure regulating port and said main discharge ports, respectively, said input port and said main discharge port of the oil only in the direction to the input port from said main discharge ports A feedback port that communicates via a first check valve that allows flow and that acts on the output port and the control port in the pressing direction, and a hydraulic operation section and the sub discharge port are connected to the sub discharge port. To the output port, the feedback port, and the hydraulic operating portion only through a second check valve that allows the flow of oil, and in the same direction as the hydraulic direction of the control port. hydraulic control system for an automatic transmission according to claim 12, characterized in that you are provided with a biasing member for applying a load.

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