CN100441462C - Electronically controllable power steering apparatus for vehicle - Google Patents
Electronically controllable power steering apparatus for vehicle Download PDFInfo
- Publication number
- CN100441462C CN100441462C CNB2006100824401A CN200610082440A CN100441462C CN 100441462 C CN100441462 C CN 100441462C CN B2006100824401 A CNB2006100824401 A CN B2006100824401A CN 200610082440 A CN200610082440 A CN 200610082440A CN 100441462 C CN100441462 C CN 100441462C
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- Prior art keywords
- valve
- spool
- automobile
- power steering
- steering apparatus
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Classifications
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- 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
- B62D5/09—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by means for actuating valves
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- 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
- B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
- B62D5/0403—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear characterised by constructional features, e.g. common housing for motor and gear box
- B62D5/0406—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear characterised by constructional features, e.g. common housing for motor and gear box including housing for electronic control unit
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- 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
- B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear
- B62D5/0409—Electric motor acting on the steering column
- B62D5/0412—Electric motor acting on the steering column the axes of motor and steering column being parallel
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D6/00—Arrangements for automatically controlling steering depending on driving conditions sensed and responded to, e.g. control circuits
- B62D6/02—Arrangements for automatically controlling steering depending on driving conditions sensed and responded to, e.g. control circuits responsive only to vehicle speed
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2400/00—Special features of vehicle units
- B60Y2400/40—Actuators for moving a controlled member
- B60Y2400/402—Manual actuators, i.e. input levers or linkages therefor
- B60Y2400/4026—Manual actuators, i.e. input levers or linkages therefor providing feel, e.g. with feedback force
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Steering Control In Accordance With Driving Conditions (AREA)
- Power Steering Mechanism (AREA)
Abstract
Provided is an electronically controllable power steering apparatus for vehicle, which comprises a hydraulic pressure counter reaction unit and a pressure control valve. The pressure control valve comprises a first valve and a second valve. The first valve comprises a first valve-body having a discharge port and a supply port in its peripheral region, a first valve core which glides in the first valve-body and has a first channel which is connected to the supply port and has a downward opening, and a first elastic part which is formed on the top part of the first valve core. The second valve comprises a hollow second valve-body having a longitudinal port in its peripheral region, a second valve core which glides in the second valve-body and has a second channel which is connected to the longitudinal port and has an upward opening, a second elastic part provided on one side of the second valve core, and a solenoid provided on the other side of the second valve core. Under the control of the first valve and the second valve, drivers are capable of apperceiving an obvious sensing difference of steering deriving from speed changes of vehicles.
Description
Technical field
The present invention relates to a kind of electronically controllable power steering apparatus that is used for automobile.More particularly, the present invention relates to a kind of electronically controllable power steering apparatus that is used for automobile, this electronically controllable power steering apparatus has pressure-gradient control valve, this pressure-gradient control valve comprises first valve and second valve, this first valve is used for the maximum reaction pressure of the working fluid of control action on hydraulic pressure counteraction unit (hydraulic reaction unit), this second valve is used for regulating reaction pressure according to car speed, up to reaching maximum reaction pressure, make chaufeur perception to change the notable difference that turns to sense that produces with car speed thus.
Background technology
As everyone knows, chaufeur utilizes the steering hardware of automobile to change the sense of motion of automobile as required.Especially, steering hardware changes the centre of gration of vehicle front, and like this, automobile just advances along required direction.
Power steering gear helps chaufeur to utilize servomechanism to come the direction of operating dish, and this servomechanism has improved operating effort.As a result, chaufeur can change the route of automobile at an easy rate with less power.
Power steering gear is divided into hydraulic power steering (HPS) device and electric powered steering (EPS) device.
Under the situation of HPS device, supply with working fluid with the Hydraulic Pump that the S. A. of driving engine links to each other to clutch release slave cylinder, wherein said clutch release slave cylinder links to each other with a tooth bar.Then, clutch release slave cylinder moves its piston, and improves steering force, and like this, chaufeur can be carried out steering operation with less power.The EPS device comprises motor and electronic control unit (ECU), and with replacement liquid press pump and clutch release slave cylinder, therefore, motor has improved operating effort.
Although the automobile that recently day by day increases is equipped with the EPS device,, most of automobile still uses the HPS device.
With low cruise or when keeping static, the friction drag between tire and the road surface is bigger at automobile.This means to have sizable steering power.On the contrary, automobile run at high speed and friction drag hour, needn't need big steering power.In this, traditional HPS device has such problem, that is, though automobile with low speed or high-speed cruising, it all supplies with the steering power of same amount.As a result, when automobile ran at high speed, bearing circle was operating (or grasping) than required looser mode, and steering stability reduces.
In order to address this problem, introduce ECS Electronic Control Power Steering (ECPS) device recently, with by supply, thereby even keep steering stability when high speed according to car speed control steering power.
Fig. 1 shows the structure according to the electronically controllable power steering apparatus that is used for automobile of prior art.Fig. 2 a is the cutaway view that illustrates according to a side of the channel switching valve of prior art.Fig. 2 b is the cutaway view that illustrates according to a side of the opposite side of the channel switching valve of prior art and pressure-gradient control valve.
Shown in Fig. 1 to 2b, comprise Hydraulic Pump 101 according to the electronically controllable power steering apparatus that is used for automobile of prior art, its driving engine (not shown) by automobile drives; Hollow input shaft 203, it comprises torsion bar 201; Pinion shaft 205, it links to each other with input shaft 203 via torsion bar 201; Passage transfer valve 103, it is used for coming based on the relative displacement between input shaft 203 and the pinion shaft 205 passage of switch operating fluid; Clutch release slave cylinder 105, it is used for supplying steering power by means of the working fluid that transmits from fluid transfer valve 103; Speed sensor 107, it is used to detect the speed of automobile; Electronic control unit 109, it is used to receive the electric signal from speed sensor 107; Hydraulic pressure counteraction unit 209, it is used to utilize the relative displacement between counteraction plunger (or reaction plunger) 207 restriction input shafts 203 and the pinion shaft 205, and wherein, described counteraction plunger 207 is suitable for moving back and forth by means of hydraulic pressure; And pressure-gradient control valve 111, it places a side of passage transfer valve 103, is fed to the working fluid of hydraulic pressure counteraction unit 209 with control under the control of electronic control unit 109.
Pressure-gradient control valve 111 comprises hollow valve body 211, and it has supply port 221, discharge side 223 and feedback port 224 on the periphery of being formed at; Spring 213, it is contained in the valve body 211 near the top, to supply with downward elastic force to spool 215 (being described below); Spool 215, it has upper end of being supported by spring 213 and the lower end of being supported by screw actuator 217 (being described below), and be formed at first and second step parts 225,227 on the outer surface of spool 215, this first and second step part 225,227 has desired depth, be spaced from each other preset distance simultaneously, and be interconnected via access opening 229; Screw actuator 217, it is used under the control of electronic control unit 109 from supported underneath spool 215.
As above the basic functional principle of Gou Zao electronically controllable power steering apparatus is identical with the principle of work of conventional hydraulic power steering gear.More particularly, driver's operation bearing circle 113, steering shaft 115 rotations that therefore link to each other with bearing circle 113.Input shaft 203 rotations via a Hooke's coupling 117 links to each other with steering shaft 115 produce relative displacement with respect to pinion shaft 205 simultaneously.As a result, working fluid is supplied among the left and right 105a of pressure chamber, the 105b of clutch release slave cylinder 105 one of them selectively, and supplies with steering powers to tooth bar 119.
Yet as below will describing in detail with reference to figure 3 and 4, the operation of this electronically controlled steering device increases and changes along with car speed.
Fig. 3 and 4 shows according to the cutaway view of prior art at automobile operational circumstances of pressure-gradient control valve during respectively with low speed and high-speed cruising.
During in automobile parking or with low cruise, electronic control unit 109 receptions are by the speed signal of speed sensor 107 detections and the screw actuator 217 of control presssure control cock 111, and like this, spool 215 upwards slides.In this case, first step part 225 upward movements are also spaced apart with supply port 221, so working fluid is not sent to access opening 229.As a result, do not have working fluid to supply to hydraulic pressure counteraction unit 209, and counteraction plunger 207 separates with input shaft 203, this input shaft 203 is rotatable then, and with respect to not friction of counteraction plunger 207.This means that bearing circle 113 is loose freely operates.In other words, chaufeur can perception situation when adopting the conventional hydraulic power steering gear identical turn to sense.
During with middling speed or high-speed cruising, electronic control unit 109 receives speed signal and the control presssure control cock 111 that has been detected by speed sensor 107 at automobile, and like this, spool 215 is to lower slider.In this case, first step part 225 moves downward and is communicated with supply port 221, and like this, working fluid just is sent in the access opening 229.Working fluid is sent to hydraulic pressure counteraction unit 224 via second step part 227 and feedback port 224 from access opening 229.Because hydraulic pressure counteraction unit 209 has been supplied working fluid, the pressure by working fluid is fastened to counteraction plunger 207 on the input shaft 203, and the rotation of restriction input shaft 203.As a result, bearing circle 113 is operated difficultly.In other words, opposite with the conventional hydraulic power steering gear, chaufeur perceives the stable sense that turns to when high speed.
Fig. 5 is the graph of a relation between the pressure of input torque and the working fluid supplied with from Hydraulic Pump when being illustrated in the operation with traditional pressure-gradient control valve.Fig. 6 is the graph of a relation that illustrates between the pressure (reaction pressure) of the pressure (supply pressure) of the working fluid of supplying with from Hydraulic Pump and the working fluid the hydraulic pressure counteraction unit.
Can be clear that from Fig. 5 and 6 under the situation of traditional electronically controllable power steering apparatus, reaction pressure increases along with the increase of car speed.Especially, reaction pressure increases with car speed with being directly proportional.
In this case, chaufeur almost imperceptible difference that turns to sense when car speed changes.In other words, turn to the difference deficiency of sense so that chaufeur is grasped current riving condition.
Summary of the invention
Therefore, the present invention is suggested, to be used for solving the problems referred to above that prior art occurs, and the purpose of this invention is to provide a kind of electronically controlled steering device that is used for automobile, it has pressure-gradient control valve, this pressure-gradient control valve comprises first valve and second valve, wherein, this first valve is used for the maximum reaction pressure of the working fluid of control action on hydraulic pressure counteraction unit, this second valve is used for regulating reaction pressure according to car speed, up to reaching maximum reaction pressure, but make the chaufeur perception change the notable difference that turns to sense that produces with car speed thus.
In order to realize this purpose, a kind of electronically controllable power steering apparatus that is used for automobile is provided, this electronically controllable power steering apparatus comprises hydraulic pressure counteraction unit and pressure-gradient control valve, this hydraulic pressure counteraction unit is used to limit the relative displacement between input shaft and the pinion shaft, this pressure-gradient control valve is used for the supply of Control work fluid to hydraulic pressure counteraction unit, wherein, this pressure-gradient control valve has first valve and second valve, this first valve has hollow first valve body, first spool and first elastomeric element, this first valve body has discharge side and the supply port that is formed on its periphery, this first spool is configured to so that slide in this first valve body, and in this first spool, be formed with first passage, this first passage is communicated with this supply port and has a downward opening, this first elastomeric element is formed at the top of this first spool, this second valve has hollow second valve body, this second valve body has radial port, second spool, second elastomeric element and screw actuator, this radial port is formed on the periphery of this second valve body, this second spool is configured to so that slide in this second valve body, and in this second spool, be formed with second channel, this second channel is communicated with this radial port, and has upwards an opening, this second elastomeric element is set at a side of this second spool, this screw actuator is set at the opposite side of this second spool, wherein this first valve and this second valve are housed inside in the hollow valve casing, be secured to the inside of this valve casing simultaneously, the working fluid of supplying with from the downside of this first spool supplies to this hydraulic pressure counteraction unit via this second valve, and control the rotation of this input shaft, this valve casing has the interruption step between this first valve and this second valve.
Description of drawings
Above-mentioned and other purposes of the present invention, characteristics and advantage will become more obvious from the detailed description of hereinafter carrying out in conjunction with the accompanying drawings, wherein:
Fig. 1 shows the structure according to the electronically controllable power steering apparatus that is used for automobile of prior art;
Fig. 2 a is the cutaway view that illustrates according to a side of the passage transfer valve of prior art;
Fig. 2 b is the cutaway view that illustrates according to a side of the opposite side of the passage transfer valve of prior art and pressure-gradient control valve;
Fig. 3 is the cutaway view of the operational circumstances of pressure-gradient control valve when being illustrated in automobile with low cruise;
Fig. 4 is the cutaway view of the operational circumstances of pressure-gradient control valve when being illustrated in automobile and running at high speed;
Fig. 5 is the graph of a relation between the pressure of input shaft and the working fluid supplied with from Hydraulic Pump when the operation with traditional pressure-gradient control valve;
Fig. 6 is the graph of a relation between the pressure (reaction pressure) of the working fluid of working in the pressure (supply pressure) of the working fluid supplied with from Hydraulic Pump when the operation with traditional pressure-gradient control valve and the hydraulic pressure counteraction unit;
Fig. 7 is the cutaway view according to the pressure-gradient control valve of the first embodiment of the present invention;
Fig. 8 is the part sectional view according to first valve of the first embodiment of the present invention;
Fig. 9 is the graph of a relation between the pressure of input torque and the working fluid supplied with from Hydraulic Pump;
Figure 10 is the graph of a relation between the pressure (reaction pressure) of the pressure (supply pressure) of the working fluid supplied with from Hydraulic Pump and the working fluid of working in hydraulic pressure counteraction unit; And
Figure 11 is the cutaway view that pressure-gradient control valve according to a second embodiment of the present invention is shown.
The specific embodiment
The preferred embodiments of the present invention are described below with reference to the accompanying drawings.In following specification sheets and accompanying drawing, therefore identical identical the or similar elements of Reference numeral indication will save being repeated in this description identical or like.
Fig. 7 is the cutaway view that illustrates according to the pressure-gradient control valve of the first embodiment of the present invention.
As shown in Figure 7, comprise first valve 710 and second valve 720 according to the pressure-gradient control valve of the first embodiment of the present invention, and be contained in the valve casing 730.First valve 710 comprises hollow first valve body 701, first spool or the valve rod (spool) 703 and first elastomeric element 705, wherein, this first valve body 701 has discharge side 223 and the supply port 221 that is formed on its periphery, this first spool 703 is configured to so that slide in first valve body 701, and in first spool 703, be formed with first passage 707, and first passage 707 is communicated with (or communicating) with supply port 221, and having downward opening, this first elastomeric element 705 places the top of first spool 703.Second valve 720 comprises hollow second valve body 711, second spool 713, second elastomeric element, 715 sum spiral pipes 217, wherein, this second valve body 711 has the feedback port 224 that is formed on its periphery, this second spool is configured to so that slide in second valve body 711, and in this second spool 713, be formed with second channel 717, and second channel 717 is communicated with feedback port 224, and has upwards an opening, this second elastomeric element 715 is formed at the top of second spool 713, and this screw actuator 217 is formed under second spool 713.
To describe first valve body 701, first spool 703 and first elastomeric element 705 that constitute first valve 710 below in detail.
Fig. 8 is the part sectional view according to first valve of the first embodiment of the present invention.
As shown in Figure 8, supply port 221 can have filter 801, and this filter 801 is set at its opening part, enters first valve 710 to prevent impurity with working fluid.
Can inside part form and have the anti-blocking groove 803 of desired depth, stop up supply ports 221 so that prevent filter 801 from the outer surface of first valve body 701 to supply port 221.
First elastomeric element 705 places between the inboard on top of the upside of first spool 703 and first valve body 701, with downward vertically direction elastic force F is put on first spool 703.Product P * A of the sectional area A of the pressure P of the working fluid when act on first spool 703 from the below on and first spool 703 is during greater than the elastic force F of first elastomeric element 705, and first spool 703 is along axially moving up, and vice versa.By this way, utilize the pressure of working fluid to order about that first spool 703 is linear vertically to be moved, and allow that optionally first passage 707 is communicated with supply port 221.So just, controlled flowing of working fluid.
The working fluid of supplying with from the downside of first spool 703 also supplies to hydraulic pressure counteraction unit 209 via second valve 720, and the rotation of control input shaft 203.As mentioned above, the pressure of working fluid is controlled by operating first valve 710.
Especially, the elastic force that predeterminable first elastomeric element 705 can apply is so that the maximum pressure of control action on the downside of first spool 703.
First elastomeric element 705 is preferably made by the spring with predetermined elastic force, but is not limited to material described here.
Replacing regulating stopper 723, keeps lid (location lid) can place the top of first elastomeric element 705 and be press-fit to first valve body 701.
Be noted that the elastic force of first elastomeric element 705 is unadjustable when using maintenance to cover, but fixing, because keep lid to keep being press-fit in first valve body 701.
Yet, use to keep the advantage of lid to be, at stock production during, to compare with regulating the situation that stopper 723 is threaded onto on first valve body 701 according to pressure-gradient control valve of the present invention, its manufacturing time is lacked.
Lid 709 can be press-fit in first valve body 701.Replacedly, outside thread and negative thread can be formed, so that they are threaded respectively on the periphery of covering 709 and first valve body 701 and interior perimeter surface.
Being shaped as of second spool 713 is cylindrical, and is formed and can slides in second valve body 711.Form a second channel 717 in second spool 713, this second channel 717 is communicated with feedback port 224.Second channel 717 has the opening towards the top of second spool 713, and like this, working fluid just is sent to hydraulic pressure counteraction unit 209 via second channel 717 and feedback port 224 from first valve 710.
Second elastomeric element 715 places between the upside of inboard and second spool 713 on top of second valve body 711, and downward vertically direction puts on elastic force on second spool 713.Second elastomeric element 715 is preferably made by spring, but is not limited to material described here.
Preferably, hollow cover 709 places between the inboard on top of the upside of second elastomeric element 715 and second valve body 711, and be communicated with second channel 717, so that support second elastomeric element 715 and prevent that its inside from second valve body 711 breaks away from when the direction that screw actuator 217 is operated and second spool 713 makes progress is vertically slided, this will be explained hereinafter.Lid 709 can be press-fit in second valve body 711.Replacedly, can on outer surface that covers 709 and second valve body 711 and interior perimeter surface, form outside thread and negative thread respectively, thereby they are threaded.
During with low cruise, the direction that screw actuator 217 makes progress vertically moves second spool 713, and reduces to supply to the amount of working fluid of hydraulic pressure counteraction unit 209 at automobile, therefore, and direction of operating dish loosely.When automobile ran at high speed, the downward vertically direction of screw actuator 217 moved second spool 713, and increased the amount of working fluid supply to hydraulic pressure counteraction unit 209, therefore, and direction of operating dish tightly, and keep steering stability.
Fig. 9 is according to the graph of a relation between the pressure of the pressure-gradient control valve of first embodiment of the present invention input torque and the working fluid supplied with from Hydraulic Pump when the operation.Figure 10 is the graph of a relation between the pressure (reaction pressure) of the working fluid of working in the pressure (supply pressure) of the working fluid supplied with from Hydraulic Pump when the operation according to the pressure-gradient control valve of the first embodiment of the present invention and the hydraulic pressure counteraction unit.
From Fig. 9 and 10, can clearly be seen that, pressure-gradient control valve according to the first embodiment of the present invention is operated by this way, promptly, reaction pressure increases along with the increase of car speed, this is identical with situation of the prior art, but the ratio that reaction pressure increases changes with the increase of car speed.As a result, chaufeur can perception turn to the notable difference of sense, and grasps current riving condition at an easy rate.
Figure 11 is the cutaway view that pressure-gradient control valve according to a second embodiment of the present invention is shown.
As shown in figure 11, pressure-gradient control valve according to a second embodiment of the present invention comprises first valve 710 and second valve 720, and is contained in the valve casing 730.First valve 710 comprises hollow first valve body 701, first spool 703 and first elastomeric element 705, wherein, first valve body 701 has discharge side 223 and the supply port 221 that is formed on its periphery, first spool 703 is configured to and can slides in first valve body 701, and in first spool 703, be formed with first passage 707, so that this first passage 707 is communicated with supply port 221, and has downward opening, this first elastomeric element 705 places the top of first spool 703.Second valve 720 comprises hollow second valve body 711, second spool 713, second elastomeric element, 715 sum spiral pipes 217, wherein, this second valve body 711 extends along the axial direction perpendicular to first valve body 701, and has a communication port 1101, this communication port 1101 is formed on the periphery of second valve body 711, this second spool 713 is configured to and can slides in second valve body 711, and in this second spool 713, has second channel 717, so that this second channel 717 is communicated with this communication port 1101, and has a opening towards hydraulic pressure counteraction unit (not shown), this second elastomeric element 715 is formed at a side of second spool 713, and this screw actuator 217 is formed at the opposite side of second spool 713.
The advantage of Gou Zao pressure-gradient control valve according to a second embodiment of the present invention is in the above-described manner, and is opposite with first embodiment, owing to second valve 720 extends along the axial direction perpendicular to first valve 710, thereby can overcome the space constraint that may exist.
Other structures of pressure-gradient control valve according to a second embodiment of the present invention are identical with first embodiment with operation.Therefore, identical Reference numeral is used to indicate components identical, and will economize being repeated in this description of decorrelation here.
As mentioned above, the advantage that is used for the electronically controllable power steering apparatus of automobile according to the present invention is, it has pressure-gradient control valve, this pressure-gradient control valve comprises first valve and second valve, wherein, this first valve is used for the maximum reaction pressure of the working fluid of control action on hydraulic pressure counteraction unit, this second valve is used for regulating reaction pressure according to car speed, up to reaching maximum reaction pressure, therefore, chaufeur can perception change the notable difference that turns to sense that produces with car speed.
Although described the preferred embodiments of the present invention for the purpose of explaining, one skilled in the art will appreciate that under the situation that does not depart from the disclosed scope and spirit of the present invention of claims, can carry out various variations, additional and replacement.
Claims (14)
1. electronically controllable power steering apparatus that is used for automobile comprises:
Hydraulic pressure counteraction unit, it is used to limit the relative displacement between input shaft and the pinion shaft, and
Pressure-gradient control valve, it is used for the supply of Control work fluid to this hydraulic pressure counteraction unit, wherein,
This pressure-gradient control valve has first valve and second valve,
This first valve has hollow first valve body, first spool and first elastomeric element, this first valve body has discharge side and the supply port that is formed on its periphery, this first spool is configured to so that slide in this first valve body, and has a first passage that is formed in this first spool, this first passage is communicated with this supply port and has downward opening, and this first elastomeric element is formed at the top of this first spool; And
This second valve has hollow second valve body, second spool, the second elastomeric element sum spiral pipe, this second valve body has the radial port that is formed on its periphery, this second spool is configured to so that slide in this second valve body, and has a second channel that is formed in this second spool, this second channel is communicated with this radial port and has upwards an opening, this second elastomeric element is set at a side of this second spool, and this screw actuator is set at the opposite side of this second spool; And
This first valve and this second valve are housed inside in the hollow valve casing, are secured to the inside of this valve casing simultaneously,
The working fluid of supplying with from the downside of this first spool supplies to this hydraulic pressure counteraction unit via this second valve, and controls the rotation of this input shaft,
This valve casing has the interruption step between this first valve and this second valve.
2. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 1 is characterized in that, is provided with stopper at the top of this first elastomeric element.
3. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 2 is characterized in that, this stopper is press-fit on this first valve body.
4. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 2 is characterized in that, this stopper is threadingly attached on this first valve body.
5. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 2 is characterized in that, a bearing is set, with in abutting connection with the downside of this stopper and the upside of this first elastomeric element.
6. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 1 is characterized in that, a hollow cover is set under this first spool, and is communicated with this first passage.
7. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 6 is characterized in that, forms porose in this lid.
8. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 1 is characterized in that, is provided with filter at the opening part of this supply port.
9. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 8 is characterized in that, the inside part from the outer surface of this first valve body to this supply port forms the groove with desired depth.
10. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 9 is characterized in that, this first valve and this second valve are parallel to each other vertically.
11. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 9 is characterized in that, this first valve and this second valve are coaxial each other.
12. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 1 is characterized in that, this second valve is perpendicular to this first valve.
13. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 9 is characterized in that, a hollow cover is set at a side of this second elastomeric element, and is communicated with this second channel.
14. the electronically controllable power steering apparatus that is used for automobile as claimed in claim 1 is characterized in that, this second valve is set under this first valve.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020050099467A KR100723730B1 (en) | 2005-10-21 | 2005-10-21 | Pressure Control Valve and Electronically Controllable Power Steering Apparatus for Vehicle Including Same |
| KR1020050099467 | 2005-10-21 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1951750A CN1951750A (en) | 2007-04-25 |
| CN100441462C true CN100441462C (en) | 2008-12-10 |
Family
ID=38058360
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006100824401A Expired - Fee Related CN100441462C (en) | 2005-10-21 | 2006-05-16 | Electronically controllable power steering apparatus for vehicle |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP4350088B2 (en) |
| KR (1) | KR100723730B1 (en) |
| CN (1) | CN100441462C (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100854780B1 (en) | 2007-02-14 | 2008-08-27 | 주식회사 만도 | Filter and Pressure Control Valve of Electronically Controllable Power Steering Apparatus including Same |
| KR20130064540A (en) | 2011-12-08 | 2013-06-18 | 현대자동차주식회사 | System and method for controlling electric power steering apparatus of vehicle |
| CN102563106B (en) * | 2011-12-29 | 2013-06-05 | 厦门市易洁卫浴有限公司 | Dual control valve |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3994538A (en) * | 1975-01-28 | 1976-11-30 | Girling Limited | Hydraulic control valve assemblies for vehicle anti-skid braking systems |
| US4787469A (en) * | 1985-07-31 | 1988-11-29 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Power steering system |
| JPH06219296A (en) * | 1993-01-29 | 1994-08-09 | Koyo Seiko Co Ltd | Hydraulic power steering device |
| JPH10273063A (en) * | 1997-03-04 | 1998-10-13 | Showa:Kk | Electronic control type car speed sensitive power steering device |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100215238B1 (en) | 1996-12-07 | 1999-08-16 | 오상수 | Reaction force device for electric controlled power steering systems |
| KR100842935B1 (en) * | 2001-12-28 | 2008-07-02 | 주식회사 만도 | Power steering device |
| KR100842933B1 (en) * | 2001-12-28 | 2008-07-02 | 주식회사 만도 | Power steering device |
-
2005
- 2005-10-21 KR KR1020050099467A patent/KR100723730B1/en active IP Right Grant
- 2005-12-20 JP JP2005366632A patent/JP4350088B2/en not_active Expired - Fee Related
-
2006
- 2006-05-16 CN CNB2006100824401A patent/CN100441462C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3994538A (en) * | 1975-01-28 | 1976-11-30 | Girling Limited | Hydraulic control valve assemblies for vehicle anti-skid braking systems |
| US4787469A (en) * | 1985-07-31 | 1988-11-29 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Power steering system |
| JPH06219296A (en) * | 1993-01-29 | 1994-08-09 | Koyo Seiko Co Ltd | Hydraulic power steering device |
| JPH10273063A (en) * | 1997-03-04 | 1998-10-13 | Showa:Kk | Electronic control type car speed sensitive power steering device |
Also Published As
| Publication number | Publication date |
|---|---|
| KR100723730B1 (en) | 2007-05-30 |
| JP4350088B2 (en) | 2009-10-21 |
| KR20070043321A (en) | 2007-04-25 |
| JP2007112412A (en) | 2007-05-10 |
| CN1951750A (en) | 2007-04-25 |
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