WO2003076252A1 - Dispositif de regulation de l'ecoulement destine a une servodirection - Google Patents
Dispositif de regulation de l'ecoulement destine a une servodirection Download PDFInfo
- Publication number
- WO2003076252A1 WO2003076252A1 PCT/JP2003/002483 JP0302483W WO03076252A1 WO 2003076252 A1 WO2003076252 A1 WO 2003076252A1 JP 0302483 W JP0302483 W JP 0302483W WO 03076252 A1 WO03076252 A1 WO 03076252A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- flow control
- opening
- power steering
- flow
- electromagnetic proportional
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
- F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/062—Details, component parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/41—Flow control characterised by the positions of the valve element
- F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/455—Control of flow in the feed line, i.e. meter-in control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/465—Flow control with pressure compensation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/875—Control measures for coping with failures
- F15B2211/8752—Emergency operation mode, e.g. fail-safe operation mode
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
Definitions
- the present invention relates to a flow control device including an electromagnetic proportional flow control valve for controlling a flow guided to a power steering mechanism.
- Some vehicles have an electromagnetic proportional flow control valve to control the flow of hydraulic oil supplied to a power steering device of a vehicle.
- a large power assist force is required when the vehicle is running in a low speed range or when operating the steering wheel while the vehicle is stopped.
- the opening of the electromagnetic proportional flow control valve is increased to increase the flow rate of hydraulic oil supplied to the power steering device.
- the opening of the electromagnetic proportional flow control valve is reduced. In this case, excess hydraulic oil is released by the pressure compensating valve, bypassing the electromagnetic proportional flow control valve, thereby reducing energy loss.
- FIG. 4 is a graph showing the relationship between the control current I of the conventional electromagnetic proportional flow control valve and the flow Qc supplied to the power steering device. As shown in this graph, the flow supplied to the power steering device is set to decrease as the control current of the electromagnetic proportional flow control valve increases.
- the valve opening is set to increase as the control current of the electromagnetic proportional flow control valve decreases, in order to maintain a large valve opening even when the current cannot be supplied due to a failure or the like.
- the electromagnetic proportional flow control valve maintains a large opening by the holding force of the spring, and enables the supply of hydraulic oil to the power steering device to perform power assist. The function is maintained.
- a state in which the solenoid of the electromagnetic proportional flow control valve is excited with a large current is a state in which the power assisting power of the power steering device is not required, that is, a standby state. Takes a lot of time while driving.
- An object of the present invention is to provide a flow rate control device capable of further reducing energy loss while maintaining a fail-safe function. Disclosure of the invention
- the present invention relates to a steering flow control device, comprising: a hydraulic pump; an electromagnetic proportional flow control valve for controlling a flow rate of hydraulic oil supplied from the hydraulic pump to a power steering mechanism; A pressure compensating valve that keeps the pressure difference upstream and downstream of the valve constant and bypasses the excess flow rate.
- the electromagnetic proportional flow control valve maintains a predetermined initial opening when the control current is zero, When the control current is gradually reduced from zero, the opening decreases and the minimum opening is reached.When the control current exceeds a predetermined control current, the opening gradually increases toward the maximum opening. Has become.
- the solenoid proportional flow control valve supplies a not-so-large intermediate current that minimizes the opening. Therefore, the power consumption of the solenoid can be reduced. In this state, a small amount of hydraulic oil is supplied from the hydraulic pump to the power steering mechanism, and the remaining excess flow is returned from the upstream of the electromagnetic proportional flow control valve via the pressure compensation valve, reducing energy loss. it can.
- control current is supplied over a wide control range from the minimum opening to the maximum opening of the electromagnetic proportional flow control valve. Performs accurate flow rate proportional control according to the control current. I can.
- FIG. 1 is a circuit diagram of an embodiment of the present invention.
- FIG. 2 is a graph showing the relationship between the control current 1 and the control flow rate Qc.
- FIG. 3 is a sectional view of the electromagnetic proportional flow control valve.
- FIG. 4 is a graph showing the relationship between the control current I and the control flow rate Qc in the prior art.
- the discharge side of the hydraulic pump 7 is connected to an electromagnetic proportional flow control valve 2 via a supply flow path 1.
- a power steering mechanism PS is connected to the downstream side of the electromagnetic proportional flow control valve 2.
- the supply flow path 1 is provided with a branch flow path 3 branching from the upstream of the electromagnetic proportional flow control valve 2, and the branch flow path 3 is provided with a pressure compensating valve 4 for bypassing excess flow to a reservoir 8.
- the pressure on the upstream side of the electromagnetic proportional flow control valve 2 is introduced into one pilot chamber 4a of the pressure compensating valve 4, and the downstream of the electromagnetic proportional flow control valve 2 is introduced into the other pilot chamber 4b.
- the pressure compensating valve 4 is actuated according to the difference between these pressures and the spring force of the spring 4c, and when the pressure difference increases, the bypass flow rate increases, and the pressure increases. As the difference becomes smaller, the bypass flow rate is reduced.
- the pressure on the upstream side can be kept higher than the load pressure of the power steering mechanism PS by an amount corresponding to the panel force of the spring 4c.
- a flow proportional to the opening of the electromagnetic proportional flow control valve 2 can be supplied to the power steering mechanism PS.
- 6 is a relief valve that functions as a safety valve.
- the electromagnetic proportional flow control valve 2 has a predetermined initial opening degree shown by the elastic force of the spring F when the proportional solenoid S is not excited, that is, when the control current is zero, that is, the open position ( a) is kept.
- the exciting force of the proportional solenoid S is increased, and the opening of the electromagnetic proportional flow control valve 2 is reduced.
- the closing position (b) is reached, and the amount of supply to the power steering mechanism PS is minimized.
- the closed position (b) although it is completely closed in the figure, it is actually opened to a certain degree, allowing a small amount of hydraulic oil to flow.
- FIG. 2 is a graph showing the relationship between the control current I of the proportional solenoid S of the electromagnetic proportional flow control valve 2 and the flow Qc supplied to the power steering mechanism PS.
- the electromagnetic proportional flow control valve 2 supplies a predetermined large flow rate to the power steering mechanism PS at the initial opening when the control current supplied to the proportional solenoid S is zero.
- the control current I is increased from zero, the supply flow rate Qc decreases, and when the control current I becomes the standby current Is, the flow rate supplied to the power steering mechanism PS is the minimum, that is, Standby flow rate is QS.
- the control current I is increased from the standby state, the flow rate supplied to the power steering mechanism PS gradually increases again.
- control current I s The range from the control current I s to the maximum current is wider than the range from the control current I of zero to the control current I s in the standby state. Therefore, when the normal power assist is required, the control current I By using a control current of s or more, the proportional control accuracy of the flow rate with respect to the current value is enhanced, and the electromagnetic proportional flow control valve 2 can maintain high control performance, in other words, high resolution.
- the controller When the vehicle is running in a high speed range, that is, when the power steering mechanism PS requires little assistance, the controller (not shown) The control current I of the solenoid S is set to the standby current Is. The control flow rate of the electromagnetic proportional flow control valve 2 becomes minimum.
- control current Is for maintaining the standby flow rate is less than half that of the conventional example, so that the power consumption of the electromagnetic proportional flow control valve 2 in the standby state is also reduced. Can be.
- the electromagnetic proportional flow control valve 2 When power assistance is required in a low or medium speed range of the vehicle, the electromagnetic proportional flow control valve 2 is controlled with a control current larger than the standby control current Is. For this reason, the control flow rate of the electromagnetic proportional flow control valve 2 increases, and the power assisting force generated by the power steering mechanism P S increases, so that steering operation can be performed lightly.
- the power consumption in the standby state can be reduced while maintaining the fail-safe function.
- FIG. 3 shows a specific structure of the electromagnetic proportional flow control valve 2 in FIG.
- An assembling hole 10 is formed in the body 16 of the flow control valve, and a sleeve 40 having a hollow portion 42 is inserted into and fixed to the assembling hole 10.
- This hollow part 4 2 The sleeve 40 extends in the axial direction and penetrates, and the sleeve 40 is formed with a hole 44 communicating with the hollow portion 42 from the radial direction.
- the hole 44 is connected to the upstream channel 11 provided in the main body 16, and one end opening of the hollow portion 42 communicates with the downstream channel 12.
- the upstream flow path 11 is connected to the hydraulic pump 7 shown in FIG. 1, and the downstream flow path 12 is connected to the power steering mechanism PS.
- a coil assembly 50 is connected to a portion where the sleeve 40 protrudes from the main body 16.
- the base cylinder member 51 is connected to the sleeve 40 via a filler ring 56. Then, the hollow portion 52 of the base member 51 communicates with the hollow portion 42 of the sleeve 40.
- the shaft 30 is slidably disposed in the hollow portions 42 and 52 of these two members.
- the shaft 30 is movably supported in the axial direction by a bearing 31 fixed to the inner peripheral surface of the hollow portion 42.
- the distal end side of the shaft 30 faces the hollow portion 42 of the sleeve 40, and a plunger 37 is fitted and fixed to the outer periphery of the rear end side.
- a spring 55 is interposed between the rear end of the shaft 30 and the adjuster 54 incorporated in the center of the base member 51.
- a tapered surface 35 is formed at the tip of the shaft 30. Then, as shown in the figure, the tip of the shaft 30 having the tapered surface 35 is inserted into the cylindrical seat 41 formed in the sleeve 40, and Is blocked. However, the shaft 30 is provided with an introduction hole 32 having one end opened at the tip thereof, and a plurality of lateral holes 33 connected to the introduction hole 32 in a radial direction. These horizontal holes 33 are connected to the holes 44 of the sleeve 40 in the state shown in the drawing, whereby the upstream flow path 11 and the downstream side are passed through the introduction holes 32 and the horizontal holes 33. The flow path 12 is communicated with the flow path 12.
- a coil 53 is provided on the outer periphery of the base member 51 to constitute the proportional solenoid S.
- This state is a standby state, in which the standby flow rate Qs shown in FIG. At this time, the control current supplied to the proportional solenoid S is set to be Is.
- the flow rate is controlled by the side hole 33, but when the control current exceeds the standby current Is, the flow rate is controlled by the seat part 41 and the tip of the shaft 30. Control.
- a control current equal to or greater than the standby current Is is supplied to the electromagnetic proportional flow control valve 2 so that there is a gap between the seat portion 41 and the shaft tip.
- the flow rate can be proportionally controlled with high accuracy according to the control current.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Steering Control In Accordance With Driving Conditions (AREA)
- Power Steering Mechanism (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/504,060 US7251933B2 (en) | 2002-03-08 | 2003-03-04 | Flow rate control device for power steering |
DE60334681T DE60334681D1 (de) | 2002-03-08 | 2003-03-04 | Stromregelvorrichtung für servolenkung |
EP03743991A EP1484232B1 (en) | 2002-03-08 | 2003-03-04 | Flow control device for power steering |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002-63493 | 2002-03-08 | ||
JP2002063493 | 2002-03-08 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2003076252A1 true WO2003076252A1 (fr) | 2003-09-18 |
WO2003076252A8 WO2003076252A8 (fr) | 2004-11-18 |
Family
ID=27800193
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/002483 WO2003076252A1 (fr) | 2002-03-08 | 2003-03-04 | Dispositif de regulation de l'ecoulement destine a une servodirection |
Country Status (5)
Country | Link |
---|---|
US (1) | US7251933B2 (ja) |
EP (1) | EP1484232B1 (ja) |
CN (1) | CN100333953C (ja) |
DE (1) | DE60334681D1 (ja) |
WO (1) | WO2003076252A1 (ja) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4353190B2 (ja) * | 2006-02-27 | 2009-10-28 | コベルコ建機株式会社 | 建設機械の油圧回路 |
JP5307517B2 (ja) * | 2008-11-14 | 2013-10-02 | カヤバ工業株式会社 | ソレノイド |
US20120152377A1 (en) * | 2010-12-20 | 2012-06-21 | Caterpillar Inc. | Fluid bypass valve system |
EP2786915B1 (en) * | 2013-04-05 | 2016-05-25 | Danfoss Power Solutions Aps | Hydraulic steering arrangement |
RU182004U1 (ru) * | 2017-11-30 | 2018-07-31 | Федеральное государственное бюджетное образовательное учреждение высшего образования "Сибирский государственный автомобильно-дорожный университет" (СибАДИ) | Гидрообъемное рулевое управление |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS55102744A (en) * | 1979-01-30 | 1980-08-06 | Nissan Motor Co Ltd | Hydraulic device for car |
JPS58152663A (ja) * | 1982-03-05 | 1983-09-10 | Kayaba Ind Co Ltd | パワ−ステアリングの流量制御装置 |
JPS61101106U (ja) * | 1984-12-10 | 1986-06-27 | ||
JPS6314075U (ja) * | 1986-07-11 | 1988-01-29 | ||
JPS63154466A (ja) * | 1986-12-19 | 1988-06-27 | Nissan Motor Co Ltd | 流量制御ソレノイドバルブ |
JPH01199081A (ja) * | 1988-02-01 | 1989-08-10 | Atsugi Motor Parts Co Ltd | 電磁比例式圧力制御弁 |
JPH0374275A (ja) * | 1989-07-28 | 1991-03-28 | Mazda Motor Corp | 自動車の操舵装置 |
JPH1159451A (ja) * | 1997-08-21 | 1999-03-02 | Toyoda Mach Works Ltd | 流量制御装置 |
JP2001180507A (ja) * | 1999-12-24 | 2001-07-03 | Kayaba Ind Co Ltd | 流量制御装置 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2014795B (en) * | 1978-02-20 | 1982-06-16 | Jidosha Kiki Co | Electro-mechanical converters and control apparatus for power steering units utilizing the same |
JPS61101106A (ja) | 1984-10-23 | 1986-05-20 | Sanyo Electric Co Ltd | Agc回路の動作開始特性改善回路 |
JPS6314075A (ja) | 1986-06-28 | 1988-01-21 | 株式会社 河徳 | カセツトカゴ式乾燥機 |
EP0346352B1 (de) * | 1987-02-19 | 1991-02-06 | ZF FRIEDRICHSHAFEN Aktiengesellschaft | Hydraulikeinrichtung mit einer regelbaren pumpe |
JPH01194054A (ja) * | 1988-01-29 | 1989-08-04 | Hitachi Ltd | 分散処理システムのプログラムローデイング方式 |
US5577573A (en) * | 1993-12-16 | 1996-11-26 | Toyoda Koki Kabushiki Kaisha | Hydraulic power steering apparatus |
DE29716274U1 (de) * | 1997-09-10 | 1999-01-14 | Lorentz, Bernt, 22457 Hamburg | Überströmventil |
ATE248088T1 (de) * | 1999-12-13 | 2003-09-15 | Kayaba Industry Co Ltd | Servolenkung |
-
2003
- 2003-03-04 CN CNB038055821A patent/CN100333953C/zh not_active Expired - Fee Related
- 2003-03-04 DE DE60334681T patent/DE60334681D1/de not_active Expired - Lifetime
- 2003-03-04 US US10/504,060 patent/US7251933B2/en not_active Expired - Fee Related
- 2003-03-04 EP EP03743991A patent/EP1484232B1/en not_active Expired - Fee Related
- 2003-03-04 WO PCT/JP2003/002483 patent/WO2003076252A1/ja active Application Filing
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS55102744A (en) * | 1979-01-30 | 1980-08-06 | Nissan Motor Co Ltd | Hydraulic device for car |
JPS58152663A (ja) * | 1982-03-05 | 1983-09-10 | Kayaba Ind Co Ltd | パワ−ステアリングの流量制御装置 |
JPS61101106U (ja) * | 1984-12-10 | 1986-06-27 | ||
JPS6314075U (ja) * | 1986-07-11 | 1988-01-29 | ||
JPS63154466A (ja) * | 1986-12-19 | 1988-06-27 | Nissan Motor Co Ltd | 流量制御ソレノイドバルブ |
JPH01199081A (ja) * | 1988-02-01 | 1989-08-10 | Atsugi Motor Parts Co Ltd | 電磁比例式圧力制御弁 |
JPH0374275A (ja) * | 1989-07-28 | 1991-03-28 | Mazda Motor Corp | 自動車の操舵装置 |
JPH1159451A (ja) * | 1997-08-21 | 1999-03-02 | Toyoda Mach Works Ltd | 流量制御装置 |
JP2001180507A (ja) * | 1999-12-24 | 2001-07-03 | Kayaba Ind Co Ltd | 流量制御装置 |
Also Published As
Publication number | Publication date |
---|---|
US20060150808A1 (en) | 2006-07-13 |
EP1484232B1 (en) | 2010-10-27 |
CN100333953C (zh) | 2007-08-29 |
EP1484232A4 (en) | 2009-09-02 |
US7251933B2 (en) | 2007-08-07 |
CN1638996A (zh) | 2005-07-13 |
EP1484232A1 (en) | 2004-12-08 |
DE60334681D1 (de) | 2010-12-09 |
WO2003076252A8 (fr) | 2004-11-18 |
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