KR101749821B1 - Dual Pump type Hydraulic Control System and Automatic Transmission thereof - Google Patents

Dual Pump type Hydraulic Control System and Automatic Transmission thereof Download PDF

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Publication number
KR101749821B1
KR101749821B1 KR1020150155117A KR20150155117A KR101749821B1 KR 101749821 B1 KR101749821 B1 KR 101749821B1 KR 1020150155117 A KR1020150155117 A KR 1020150155117A KR 20150155117 A KR20150155117 A KR 20150155117A KR 101749821 B1 KR101749821 B1 KR 101749821B1
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South Korea
Prior art keywords
pressure
hydraulic
valve
pump
control
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KR1020150155117A
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Korean (ko)
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KR20170052957A (en
Inventor
송수영
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현대 파워텍 주식회사
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Priority to KR1020150155117A priority Critical patent/KR101749821B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F16H61/06—Smoothing ratio shift by controlling rate of change of fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
    • F16H57/0435—Pressure control for supplying lubricant; Circuits or valves therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0473—Friction devices, e.g. clutches or brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F16H61/06—Smoothing ratio shift by controlling rate of change of fluid pressure
    • F16H61/065—Smoothing ratio shift by controlling rate of change of fluid pressure using fluid control means
    • F16H61/067—Smoothing ratio shift by controlling rate of change of fluid pressure using fluid control means using an accumulator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/14—Control of torque converter lock-up clutches

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Transmission Device (AREA)

Abstract

The automatic transmission of the present invention includes a low pressure hydraulic circuit for supplying a hydraulic pressure of 2 to 9 bar generated by the mechanical oil pump 13 to a control pressure required by a torque converter (T / C) 11, an electric pump 31 Pressure hydraulic system 1-1 that is divided into a high-pressure hydraulic circuit that supplies the hydraulic pressure of 14 to 28 bar generated by the accumulator 33 to the high-pressure operating pressure required by the clutch 21 and the brake 23 at the time of shifting, It is possible to reduce the pressure load and the driving loss of the mechanical oil pump 13 driven at all times by applying the electric motor 31. The electric pump 31 driven at the time of shifting or when necessary is connected to the accumulator 33, So that the load of the electric pump 31 can be reduced and the driving loss can be reduced.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a dual-pump type hydraulic control system and an automatic transmission using the dual-

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic control system, and more particularly, to a hydraulic control system of a pump type that employs an accumulator and an automatic transmission using the same.

Generally, the hydraulic control system of an automatic transmission operates to select a friction element through a control valve and operate the hydraulic pressure generated from the oil pump so that an appropriate shift can be automatically performed according to the running state of the vehicle.

3 shows a hydraulic control system of a general automatic transmission.

As shown in the figure, the hydraulic control system includes a plurality of valves, which are connected to a torque converter (T / C) 11, a cooler 15, a clutch 21 and a brake 23, A hydraulic circuit constitutes a hydraulic circuit, and one mechanical oil pump (13-1) is driven together with the engine to supply the flow rate. The valves include a TCV (T / CON CONTROL VALVE) / regulator valve 16-1, a REDUCTION VALVE 17-1, a solenoid valve 18-1, a D A control valve 19, a manual valve 25, a pressure control valve 26, a switch valve 27, a fail safe valve 26, ) ≪ / RTI >

For example, the hydraulic control system receives a flow rate from a mechanical oil pump 13 driven by engine drive, and generates a pressure (line pressure) necessary for the system in the regulator valve 16-1. The line pressure is transmitted to the manual valve 25 which is interlocked with the driver's shift intention and restrained by the Parking-Rev-Neutral-Drive passage. The TCV 16-1 and the D / C control system valve 19 are controlled in a low pressure region to control the T / C 11 and the D / C and the line pressure to send the amount of lubricant. The solenoid valve 18-1 indirectly controls or directly controls, if necessary, the PCV 26 which receives the pressure of the pressure reducing valve 17-1 which reduces the pressure to a low pressure and generates a control pressure necessary for the actual control element. Then, the clutch 21 and the brake 23, which are capable of implementing and interrupting each step change as the H / W functioning to connect / disconnect the powertrain structure, are supplied with the pressure according to the respective gear range conditions of the PRND and released And the step-variable shifting is performed.

Korean Patent Laid-Open Publication No. 10-1999-0039769 (June 05, 1999)

However, a mechanical oil pump is a supply source that generates the maximum flow rate and hydraulic pressure required by the system. When a high pressure is required, it is the maximum load condition. Usually, it is discharged according to the rpm of the engine. In particular, the automatic transmission is capable of transmitting power even at a pressure lower than the pressure required for shifting after completion of actual shifting. However, the mechanical pump driven at all times determines the discharge flow rate according to the rpm of the engine, So that it causes a lot of driving loss.

For example, the clutch 21 and the brake 23, which serve to transmit the necessary drive torque in shifting when the automatic transmission performs a necessary shift in the vehicle, require a high control pressure if necessary. On the other hand, the T / C 11 (and D / C) is controlled by the system to a pressure lower than the hydraulic pressure required for shifting, so that even if the regulated maximum pressure is supplied from the regulator valve 16-1, Control by low pressure causes power loss.

Moreover, since the hydraulic pressure required for the control of the T / C 11 (and D / C) is controlled to the secondary T / C pressure by receiving the primary pressure controlled by the regulator valve 16-1, loss is caused In particular, the amount of lubricating oil associated with the cooler 15 can be reduced if a low pressure of 2 bar is used. However, since the T / C pressure is not supplied, the loss is inevitable.

In view of the above, the present invention provides a relatively small mechanical pump that supplies only a relatively low pressure to the T / C and D / C, while an on-demand type electric pump provides relatively high pressure to the clutch and brake only when necessary. The present invention relates to a hydraulic pump control system and a hydraulic control system for a hydraulic pump that can reduce the load of the electric pump and reduce the drive loss by connecting the electric pump driven at the time of shifting or when necessary to the accumulator which is a high- .

In order to achieve the above object, the present invention provides a hydraulic control system comprising a mechanical oil pump for generating a hydraulic pressure required for a control pressure required by a torque converter (T / C) A low pressure hydraulic circuit; A high-pressure hydraulic circuit having an electric pump for generating a hydraulic pressure for a high-pressure operating pressure required for a shifting operation element to be higher than the control pressure, and connecting the electric pump and the operating element; Is included.

In a preferred embodiment, the hydraulic pressure of the mechanical oil pump is 2 to 9 bar and the hydraulic pressure of the electric pump is 14 to 28 bar.

In a preferred embodiment, the electric pump is of a small on demand type and is associated with an accumulator, the accumulator is filled with the high pressure of the electric pump, and the line connecting the electric pump and the accumulator Way valve, and the one-way valve serves to prevent the high-pressure flow rate of the fluid filled in the accumulator from being lost when the electric pump is stopped. The one-way valve is a check valve or a check ball valve.

As a preferred embodiment, the low-pressure hydraulic circuit includes a TCV for generating a pressure required for controlling the T / C, a pressure reducing valve for lowering the line pressure, a solenoid valve for controlling the hydraulic pressure supplied from the pressure reducing valve, And a D / C control valve for controlling the D / C directly connected to the turbine in accordance with the relationship between the number of revolutions of the turbine and the idle speed.

In a preferred embodiment, the high-pressure hydraulic circuit includes a manual valve in which the pressure oil of the operating pressure is supplied through the valve body in accordance with a selected range of gear range, a control pressure upon shifting to supply the operating pressure to the operating element PCV, a switching valve for switching the operating pressure according to the quantity of the operating element, and a fail-safe valve for implementing fail-safe in hardware failure of the operating element.

In order to achieve the above object, the automatic transmission of the present invention includes a low-pressure portion controlled by a hydraulic pressure of 2 to 8.5 bar, an accumulation portion controlled by an oil pressure of 14 to 28 bar, and a shift control portion controlled by an oil pressure of 13 to 20 bar Equipped with a separate hydraulic control system; The hydraulic control system includes a mechanical oil pump in which a hydraulic pressure for a control pressure required by the T / C is generated, a TCV for generating a pressure required for controlling the T / C, a pressure reducing valve for lowering the line pressure, A low-pressure hydraulic circuit including a D / C control valve for controlling a D / C directly connected to the rotation speed of the turbine of the T / C and idling water; A hydraulic pump for generating a hydraulic pressure for a high-pressure operating pressure required for the shifting action element to be higher than the control pressure, a manual valve for supplying the pressure oil of the operating pressure via the valve body in accordance with the selected gear range, A switching valve for switching the operating pressure according to the quantity of the operating element, a fail-safe valve for implementing fail-safe in the hardware failure of the operating element, Pressure hydraulic circuit including a high-pressure hydraulic circuit.

In a preferred embodiment, the shift control portion includes a clutch and a brake as a transmission operating element. Wherein the electric pump is connected to an accumulator, the accumulator is filled with a high pressure of the electric pump, and a line connecting the electric pump and the accumulator is provided with a one-way valve, So that the flow rate of the high pressure filled in the accumulator is not lost.

The automatic transmission according to the present invention realizes the following advantages and effects by implementing a hydraulic control system with a small mechanical pump for low pressure, an on-demand electric pump for high pressure, and an accumulator for high pressure filling.

First, the driving loss is reduced by reducing the pressure load among the loads of the always-driven mechanical pumps. Second, the drive pump is driven only when a shift or a required high-pressure flow rate is required, thereby reducing drive loss. Third, unnecessary pressure loss is reduced by lowering the source pressure of the amount of lubricating oil used for lubrication. Fourth, since the high pressure fluid filled in the accumulator can be used even when the engine is off, the ISG function can be implemented. Fifth, by minimizing the application of the spool valve in the hydraulic control system, it is possible to improve the efficiency by reducing the influence of the leak. Sixth, the concept of the hydraulic control system eliminates the correlation between the shift control unit and the T / Con control unit, thereby reducing the malfunction and performance degradation in the special case through the system independence.

FIG. 1 is a block diagram of a pump duplexing hydraulic control system according to the present invention, FIG. 2 is a configuration diagram of an automatic transmission to which a hydraulic control system of a pump duplexing method according to the present invention is applied, FIG. Hydraulic control system.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings, which illustrate exemplary embodiments of the present invention. The present invention is not limited to these embodiments.

1 shows a block configuration of a hydraulic pump control system according to the present embodiment.

As shown in the figure, the hydraulic control system 1-1 is divided into a low-pressure hydraulic circuit using the hydraulic pressure of the mechanical oil pump 13 and a high-pressure hydraulic circuit using the hydraulic pressure of the electric pump 31. [

Specifically, the low-pressure hydraulic circuit uses a hydraulic pressure of about 2 to 9 bar as a line pressure, and includes a T / C (Torque Converter) 11, a mechanical oil pump 13, a cooler 15, , 17, 18, 19). The T / C 11 is a torque converter of an automatic transmission, and includes a damper clutch (D / C). The mechanical oil pump 13 is always driven by the engine drive to generate a hydraulic pressure of 2 to 9 bar. The cooler 15 cools the ATF (Automatic Transmission Fluid) circulating the T / C 11. The valves 16, 17, 18, and 19 are a TCV (T / CON CONTROL VALVE) 16 that generates a pressure required for controlling the T / C 11, a low pressure A SOLENOID VALVE 18 for controlling the operating pressure supplied from the pressure reducing valve 17 and a solenoid valve 18 for controlling the operating pressure of the T / And a D / C (D / Clutch) control valve 19 for controlling the D / C.

Specifically, the high-pressure hydraulic circuit uses an oil pressure of approximately 14 to 28 bar as a line pressure and includes an electric pump 31, an accumulator 33, and high-pressure valves 25, 26, 27, do. The electric pump 31 is a small-sized electric pump of on demand type and includes a clutch 21 and a brake 23 serving as an operating element for transmitting necessary drive torque in shifting ) To provide the line pressure. The accumulator 33 stores the high-pressure flow rate generated by the electric pump 31, and supplies a high control pressure required for shifting without driving the electric pump 31. The valves (25, 26, 27, 28, 33) include a manual valve (25) in which a working pressure oil is supplied through a valve body in accordance with a gear range selected by the driver, A PCV (Pressure Control Valve) 26 for generating and supplying a control pressure for causing the clutch 21 and the brake 23 to exhibit a smooth shifting feeling, a clutch 21 and a brake A switching valve (27) provided in an appropriate quantity in accordance with the quantity of the fuel supplied to the engine (23), and a member which should not be caught by the input element or the reaction force element at the time of shifting, A fail safe valve 28 and a one-way valve 35 for preventing the high-pressure flow rate charged in the accumulator 33 from being lost when the electric pump 31 is turned off. Particularly, the one-way valve 35 applies a check valve or a check ball valve.

2 shows a circuit configuration of the automatic transmission 1 to which the hydraulic control system 1-1 is applied.

As shown in the figure, the automatic transmission 1 includes a low-pressure portion 10 having low-pressure hardware that supplies a control pressure to the T / C 11, a shift 21 that uses the clutch 21 and the brake 23 as operating elements, Pressure hydraulic unit in which low-pressure and high-pressure hardware are installed, and low-pressure and high-pressure hydraulic lines are connected to a line (not shown) by a control unit 20, a clutch 21 and a brake 23, And a hydraulic control system 1-1 for supplying the hydraulic pressure to the hydraulic control system 1-1.

Specifically, the hydraulic control system 1-1 is the same as the hydraulic control system 1-1 described with reference to FIG. Therefore, the automatic transmission 1 is operated as follows. The low pressure section 10 generates a hydraulic pressure of about 2 to 8.5 bar by the mechanical oil pump 13 and supplies the hydraulic pressure to the T / C 11. The accumulating portion 30 generates an oil pressure of about 14 to 28 bar by the electric pump 31 or the accumulator 33 to generate an oil pressure of about 13 to 20 bar required by the clutch 21 and the brake 23 of the transmission control portion 20. [ . Particularly, the electric pump 31 is driven when the accumulator 33 is at a level of 14 bar, while the line is 16 bar, the accumulator 33 is filled with a high pressure and the driving torque of the electric pump 31 is taken into consideration When the hydraulic level is proper, it is turned off. By installing a separate pressure sensor for sensing the pressure level of the accumulator 33, the electric pump 31 can be driven only when a shift or a required high-pressure flow rate is required. Otherwise, the drive loss can be reduced by turning off.

As a result, the shift control unit 20 controls the required line pressure at the high-pressure flow rate of the accumulator 33 instead of the regulator valve that controls the required line pressure. As a result, the transmission control unit 20 can reduce the clearance for minimizing the leakage of the ATF due to the use of the high-pressure flow rate of the accumulation unit 30, and particularly, the use of the unnecessary spool valve Can be minimized. The low pressure portion 10 receives the flow rate controlled by the regulator valve at a high pressure and uses the T / C pressure that is secondarily controlled by the TCV to be supplied to the T / C 11 (and the D / C side Pressure control is performed in which the flow rate of the relatively low pressure is supplied at a relatively small flow rate of the load. Therefore, the load of the mechanical oil pump 13 driven at all times can be reduced, and in particular, the driving loss can be reduced.

As described above, in the automatic transmission according to the present embodiment, the hydraulic pressure of 2 to 9 bar generated by the mechanical oil pump 13 is supplied to the low-pressure hydraulic circuit Pressure hydraulic circuit that supplies the hydraulic pressure of 14 to 28 bar generated by the electric pump 31 or the accumulator 33 to the high-pressure hydraulic pressure required by the clutch 21 and the brake 23 at the time of shifting, It is possible to reduce the pressure load and the driving loss of the mechanical oil pump 13 which is constantly driven by applying the control system 1-1. In particular, the electric pump 31, which is driven at the time of shifting or when necessary, It is possible to reduce the load of the electric pump 31 and to reduce the drive loss by connecting with the accumulator 33.

1: Automatic transmission 1-1: Hydraulic control system
10: Low pressure part 11: T / C (Torque converter)
13: Mechanical oil pump 15: Cooler
16,16-1: TCV (T / CON CONTROL VALVE)
17, 17-1: Pressure Reducing Valve 18, 18-1: Solenoid Valve (Solenoid Valve)
19: D / C (D / Clutch) control valve
20: shift control portion 21: clutch
23: Brake 25: Manual valve (MANUAL VALVE)
26, 26-1: PCV (Pressure Control Valve)
27: Switching valve (SWITCH VALVE)
28: Fail Safe Valve
30: accumulating part 31: electric pump
33: accumulator 35: one-way valve

Claims (11)

A low pressure hydraulic circuit having a mechanical oil pump for generating a hydraulic pressure for a control pressure required by a torque converter (T / C), and connecting the mechanical oil pump and the T / C;
And a high-pressure hydraulic circuit having an electric pump for generating a hydraulic pressure for a high-pressure operating pressure required for a shifting operation element to be higher than the control pressure, and connecting the electric pump and the operating element,
The low-pressure hydraulic circuit includes a TCV (T / CON CONTROL VALVE) for generating a pressure required to control the T / C, a REDUCTION valve for reducing the hydraulic pressure of the mechanical oil pump to line pressure, And a D / C control valve for controlling a D / C (Damper Clutch) which is directly connected with the rotation speed of the turbine of the T / C in relation to the idle water, wherein the solenoid valve controls the hydraulic pressure of the turbine;
Wherein the high-pressure hydraulic circuit includes a manual valve in which the pressure oil of the operating pressure is supplied through the valve body according to a selected range of gear range, a PCV that generates the control pressure in shifting and supplies the operating pressure to the operating element A pressure control valve, a switching valve for switching the operating pressure according to the quantity of the operating element, and a fail safe valve for implementing a fail safe in the hardware failure of the operating element.
Wherein the pump control system comprises:
The system of claim 1, wherein the hydraulic oil pressure of the mechanical oil pump is 2 to 9 bar.
The pump control method according to claim 1, wherein the hydraulic pressure of the electric pump is 14 to 28 bar.
The pump control system according to claim 3, wherein the electric pump is an on demand type pump control system,
The pump control method according to claim 1, wherein the electric pump is connected to an accumulator, and the accumulator is filled with a high pressure of the electric pump.
[Claim 6] The method according to claim 5, wherein a one-way valve is provided in a line connecting the electric pump and the accumulator, and the one-way valve serves to prevent a high-pressure flow rate filled in the accumulator when the electric pump is stopped Pump two-way hydraulic control system,
The pump control method according to claim 6, wherein the one-way valve is a check valve or a check ball valve,
delete delete A hydraulic control system according to any one of claims 1 to 7,
Wherein the hydraulic pressure control system is divided into a low pressure portion controlled by hydraulic pressure of 2 to 8.5 bar, an axial pressure portion controlled by hydraulic pressure of 14 to 28 bar, and a transmission control portion controlled by hydraulic pressure of 13 to 20 bar.
11. The automatic transmission as set forth in claim 10, wherein the shift control portion comprises a clutch and a brake as a transmission operation element.
KR1020150155117A 2015-11-05 2015-11-05 Dual Pump type Hydraulic Control System and Automatic Transmission thereof KR101749821B1 (en)

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107965565B (en) * 2017-10-31 2020-04-14 中国第一汽车股份有限公司 Hydraulic lubricating system of automatic transmission of wet clutch and control method thereof
CN110486457B (en) * 2018-06-26 2022-11-01 贵州大学 Locking and cooling lubrication hydraulic system of heavy type hydraulic automatic transmission
CN110388452B (en) * 2019-07-26 2021-07-30 奇瑞汽车股份有限公司 Hydraulic supply system, control method and automobile

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010151240A (en) * 2008-12-25 2010-07-08 Toyota Motor Corp Hydraulic control device

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010151240A (en) * 2008-12-25 2010-07-08 Toyota Motor Corp Hydraulic control device

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