JP2005315271A - Hydraulic feeder - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic feeder capable of make use of an electric oil pump having a compact size and small capacity. <P>SOLUTION: First and second check valves preventing the transmission of oil pressure from one oil pump to the other oil pump are arranged on outlet-side oil passages of a main oil pump and the electric oil pump of the hydraulic feeder. An electromagnetic control valve intercepting the oil passages while turning on electricity is arranged on oil passages of a lubricating system and a cooling system located at a downstream side of the junction of the oil passages from the oil pump and electric oil pump. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a hydraulic pressure supply device, and more particularly, to a hydraulic pressure supply device for a vehicle including two or more oil pumps.

  In a vehicle hydraulic supply system, the engine is connected to the drive shaft from the engine and mechanically in order to compensate for the lack of oil pressure and oil quantity at the time of automatic stop of the engine for the purpose of saving fuel and reducing exhaust emission, and at low speed. In addition to the main oil pump, an electric oil pump is arranged in parallel so that it can be operated in an auxiliary manner. For example, Japanese Patent Laid-Open No. 2002-310272 introduces a two-pump hydraulic supply device that can use a sensorless brushless DC motor as an electric pump (auxiliary hydraulic pump).

  FIG. 3 is a diagram showing the configuration of the hydraulic pressure supply device described in the above publication. Referring to FIG. 3, the main oil pump 71 and the electric oil pump 73 driven by the electric motor 72 are arranged in parallel with respect to the load 9, and the discharge side oil passage of the electric oil pump 73 has a check A valve 74 is provided to prevent transmission of hydraulic pressure from the main oil pump 71 to the electric oil pump 73 side. However, in the configuration of FIG. 3, a valve or the like that prevents transmission of hydraulic pressure from the electric oil pump 73 to the main oil pump 71 side is not provided, and the hydraulic pressure is increased when the electric oil pump 73 is operated. Since the oil is transmitted to the 71 side, the oil leaks from the main oil pump 71 and an extra amount of oil is required. The electric oil pump of this type of hydraulic supply device is an auxiliary one that supplies hydraulic pressure while the main oil pump is stopped when the engine is stopped. However, it is suitable for two types of loads such as shift control and lubrication / cooling. Therefore, it can be said that it is premised on the adoption of a large capacity capable of securing a sufficient flow rate.

JP 2002-310272 A

  In the configuration described in the above publication, it is desired to employ a small capacity type electric oil pump that is advantageous in terms of power consumption and cost. In this case, the hydraulic pressure and oil for clutch engagement / release control in the automatic transmission are used. There is a problem that it is difficult to ensure cooling and lubricating capacity by circulating oil in each part of the vehicle while securing the amount.

  In addition, the large-capacity electric oil pump invites not only power consumption but also a situation in which the size of the battery is increased and restrictions on power management increase.

  The present invention has been made in view of the above circumstances, and its object is to make it possible to use a small-capacity type electric oil pump so as to improve the mounting property on a vehicle and to provide a hydraulic pressure supply target. An object of the present invention is to provide a hydraulic pressure supply device that can reduce the power consumption of the electric oil pump and reduce the energy consumption of the entire vehicle by making it variable.

  According to a first aspect of the present invention that provides means for solving the above problems, main oil is driven by a vehicle engine and supplies hydraulic oil to each mechanism of the vehicle including a shift control mechanism at a predetermined hydraulic pressure. In a hydraulic supply device including a pump and an electric oil pump capable of supplying hydraulic oil to a discharge oil passage of the main oil pump at a predetermined oil pressure, a speed change is performed in the oil passage as necessary during gear change control. Provided is a hydraulic pressure supply device that can prioritize the hydraulic pressure supply to the control oil passage. First and second check valves for preventing the oil flow from one oil pump to the other oil pump are disposed in the oil passage on the discharge side of the main oil pump and the electric oil pump of the hydraulic pressure supply device. An electromagnetic control valve capable of closing operation is provided in at least one system of oil passages downstream of the junction of the discharge oil passages of the main oil pump and the electric oil pump and excluding the oil passage for shift control. Is disposed. More preferably, the electromagnetic control valve is disposed in an oil passage of a lubrication system and a cooling system, and the check valve prevents transmission of hydraulic pressure to the main oil pump, and energizes the electromagnetic control valve to perform a closing operation. Therefore, priority is given to the supply of hydraulic pressure to the oil passage for shift control.

  According to the present invention, in an oil pressure supply apparatus that includes a main oil pump driven by an engine and an auxiliary electric oil pump and generates oil pressure by the electric oil pump when the engine is stopped, Of the clutch control mechanism (clutch control device, clutch piston chamber) and the cooling mechanism and lubrication mechanism of each part of the vehicle, the oil path to the latter is closed by an electromagnetic valve, and the engagement pressure and the amount of pressure oil of the clutch element of the automatic transmission Is preferentially maintained. As a result, even with a small capacity type electric oil pump, when the engine stops due to an idling stop function or the like and the main oil pump does not generate hydraulic pressure, a shift shock due to insufficient engagement hydraulic pressure of the clutch element is generated. It can be avoided.

  In addition, when the solenoid valve provided in the middle of the oil passage to the cooling mechanism and the lubrication mechanism is closed, the power consumption of the electric oil pump required for maintaining the engagement force of the clutch element is dramatically higher than when the solenoid valve is open. In addition, it is possible to suppress energy consumption in the entire vehicle and to reduce the size of the battery, thereby improving the mounting capability of the hydraulic pressure supply device on the vehicle.

  In addition, since the solenoid valve can be used to change the hydraulic pressure supply destination, it can be used in the middle of the oil path to the cooling and lubrication mechanisms when idling is stopped or when the engine is stopped by driving a hybrid vehicle alone. By closing the provided solenoid valve, it is possible to preferentially maintain the engagement pressure and pressure oil amount of the clutch element of the automatic transmission, and the solenoid valve is kept closed for a predetermined period of time. When it is necessary to supply hydraulic pressure to the mechanism, the electromagnetic valve can be opened, and power consumption management according to the state of the vehicle is possible.

  Subsequently, a preferred embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a hydraulic circuit diagram showing a configuration of an embodiment of a hydraulic pressure supply apparatus according to the present invention. Referring to FIG. 1, a hydraulic pressure supply device 7 is driven by a main oil pump 71 that is mechanically connected to and interlocked with a drive shaft of an engine (not shown), and an electric motor (also referred to as an oil pump motor) 72 including a brushless motor. The hydraulic oil in the oil pan 70 can be pumped to the loads 9a and 9b.

  Check valves (check valves) 74 and 74A are provided on the discharge side oil passage of the main oil pump 71 and the discharge side oil passage of the electric oil pump 73, respectively. Therefore, the main oil pump 71 can supply hydraulic oil to the loads 9a and 9b with a predetermined hydraulic pressure while preventing a reverse flow by a check valve (check valve) 74. Similarly, the electric oil pump 73 can supply hydraulic oil at a predetermined hydraulic pressure to the loads 9a and 9b under the backflow prevention by the check valve (check valve) 74A.

  Here, the load 9a is a load of a lubrication system such as a torque converter and each lubrication mechanism and a cooling system such as a cooling oil passage of a motor coil, and the load 9b selectively selects a friction engagement element of the automatic transmission. This is a load of a shift control system such as a clutch control solenoid and a shift control solenoid for controlling engagement and disengagement (non-engagement) at a predetermined pressure. An electromagnetic control valve 76 and an orifice 77 are disposed in the oil passage leading to the load 9a ahead (downstream) from the junction of the discharge-side oil passages of the main oil pump 71 and the electric oil pump 73. .

  The electromagnetic control valve 76 is a normally open solenoid valve that operates by excitation of a solenoid and closes when energized. Therefore, it is possible to shut off the oil passage to the load 9a side by energizing the solenoid, and it is possible to supply hydraulic pressure to the load 9a side by making it non-energized. .

  FIG. 2 is a timing chart for explaining the operation of the hydraulic pressure supply device 7 according to the present invention when mounted on a vehicle (also referred to as a hybrid vehicle) provided with two drive sources of an engine and a motor generator. This shows the operation of each solenoid while the vehicle is traveling by a motor alone, that is, during EV traveling. First, when the clutch control solenoid (clutch control SOL) is switched from the engaged state to the disengaged state, the hydraulic pressure supply device 7 switches the limit solenoid (limit SOL) for closing the electromagnetic control valve 76 from the OFF state to the ON state. And the oil path to the load 9a side is shut off (time point t1).

  A series of shift control is performed, such as switching from the engaged state of the clutch control solenoid (clutch control SOL) to the disengaged state, shifting to a predetermined shift stage by operation of the shift control solenoid, and engagement of the clutch. Continues to hold the limit solenoid (limit SOL) in the ON state (time t2 to t5).

  The hydraulic pressure supply device 7 restricts the electromagnetic control valve 76 to be closed when a predetermined time has elapsed (time t6) after the clutch control solenoid (clutch control SOL) is switched from the disengaged state to the engaged state. The solenoid (restricted SOL) is switched from the ON state to the OFF state, and the blocking of the oil passage to the load 9a side is completed.

  As described above, when the hydraulic pressure or the amount of oil to the load 9b is required, the hydraulic pressure supply device 7 blocks the oil path to the load 9a prior to (or at least simultaneously with) the operation of the solenoid of the shift control system. In order to perform the operation of turning on the limit solenoid (limit SOL), the hydraulic pressure from the electric oil pump 73 is efficiently supplied to the load 9b of the shift control system in combination with the backflow prevention by the check valve 74A. .

  In general, the output capacity (oil amount) of the electric oil pump determines the cooling capacity and lubrication capacity of the hydraulic operating mechanism corresponding to the load of the lubrication / cooling system (load 9a in the above embodiment), and the load of the transmission control system The shift speed and clutch engagement / disengagement speed of the hydraulic operation mechanism corresponding to (the load 9b in the above embodiment) are determined. As described above, the oil passage to the load of the lubrication / cooling system (load 9a in the above embodiment) is interrupted as necessary at the time of shifting, and the reverse flow to the main oil pump side is also prevented. According to the configuration, it is not necessary to use a large-capacity electric oil pump. The size reduction and capacity reduction of the electric oil pump brings a cost reduction effect that is greater than the additional cost of the check valve (check valve) and the electromagnetic control valve according to the present invention.

  Further, according to the present invention, functional disadvantages due to the size reduction and capacity reduction of the electric oil pump are minimized. The reason is that the load of the hydraulic pressure supply device is divided into a load of the lubrication / cooling system (load 9a in the above embodiment) and a load of the shift control system (load 9b in the above embodiment), and the difference This is because it is possible to control supply of appropriate hydraulic pressure according to the conditions. Although the former load requires a long flow rate, the former load does not cause adverse effects on the system (insufficient lubrication or insufficient cooling) when the flow is stopped for a short period of several minutes at the longest. If the load is sufficient to supply the oil amount in a short period of time equal to or less than the flow stop time for the former load, the load has a capacity sufficient to operate only the load of the speed change control system (load 9b in the above embodiment). If it is an electric oil pump, the adverse effect on the system is limited.

  In the above-described embodiment, since the present invention is implemented using the normally open solenoid valve, it is possible to prevent a situation in which the oil passage is shut off at the time of failure. .

  As described above, the present invention has been described in detail by exemplifying the operation in a vehicle equipped with two drive sources of the engine and the motor generator for convenience of explanation, but the technical scope of the present invention is limited. is not. The present invention can be applied to various apparatuses by changing the detailed configuration of various details within the scope of the matters described in the claims. For example, as described in Japanese Patent Application Laid-Open No. 2002-310272, a relief valve (see 75 in FIG. 3) may be provided between the check valve 74 and the electric oil pump.

1 is a hydraulic circuit diagram illustrating a configuration of a hydraulic pressure supply device according to an embodiment of the present invention. It is a timing chart for demonstrating operation | movement of the hydraulic supply apparatus which concerns on one embodiment of this invention. It is a hydraulic circuit diagram showing the structure of the conventional hydraulic pressure supply apparatus.

Explanation of symbols

7 Hydraulic supply device 9, 9a, 9b Load 70 Oil pan 71 Main oil pump 72 Electric motor (oil pump motor)
73 Electric oil pump 74, 74A Check valve 75 Relief valve 76 Electromagnetic control valve 77 Orifice

Claims (2)

A main oil pump that is driven by a vehicle engine to supply hydraulic oil to each mechanism of the vehicle including a shift control mechanism at a predetermined hydraulic pressure, and the hydraulic oil is supplied to the discharge oil passage of the main oil pump at a predetermined hydraulic pressure. In a hydraulic pressure supply device including an electric oil pump that can be supplied,
A first check valve and a second check valve arranged in oil passages on the discharge side of the main oil pump and the electric oil pump, respectively, for preventing oil flow from one oil pump to the other oil pump;
An oil passage downstream from the junction of the oil passages on the discharge side of the main oil pump and the electric oil pump, which is disposed in an oil passage other than the oil passage communicating with the speed change control mechanism, and is closed to operate the speed change control. An electromagnetic control valve that can prioritize the hydraulic supply to the mechanism,
A hydraulic supply device characterized by. The hydraulic pressure supply device according to claim 1,
The electromagnetic control valve shuts off an oil passage other than an oil passage communicating with the shift control mechanism when energized;
A hydraulic supply device characterized by.

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