CN203142767U - Speed following overflow valve - Google Patents
Speed following overflow valve Download PDFInfo
- Publication number
- CN203142767U CN203142767U CN 201320190110 CN201320190110U CN203142767U CN 203142767 U CN203142767 U CN 203142767U CN 201320190110 CN201320190110 CN 201320190110 CN 201320190110 U CN201320190110 U CN 201320190110U CN 203142767 U CN203142767 U CN 203142767U
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- Prior art keywords
- piston
- valve body
- valve
- fast
- steering
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- Expired - Fee Related
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Abstract
The utility model provides a speed following overflow valve, comprising a piston body, a valve body and a spring, wherein one end of the valve body is provided with a pressure input port; the other end of the valve body is provided with a closed end; the piston body is arranged in the valve body; an oil inlet and an oil outlet are arranged in the two sides of the valve body; and the spring is arranged between the closed end of the valve body and one end of the piston body. When a hydraulic controlled power-assisted steering automobile drives at high speed, the hydraulic controlled power-assisted steering effect can be effectively reduced, the road feel of a driver can be improved, the steering is stable and does not float, the cost is lower, and the defect of large high-speed power-assisted effect of the hydraulic controlled power-assisted steering can be well overcome.
Description
Technical field
The utility model relates to a kind of work-saving device, particularly a kind of hydraulic power-assisted steering automobile reduce the effect of high-speed hydraulic power steering with fast by pass valve.
Background technologyHydraulic power-assist steering system has had semicentennial developing history till now, and technology is very ripe, is widely used.Hydraulic power-assist steering system is made up of two parts such as hydraulic pressure and machineries, and it is with the hydraulic oil transmission medium that is used as power, and produce power by Hydraulic Pump and promote manual steering gear, thereby realize turning to.
Portability when guaranteeing that automobile pivot stud or low speed turn to, the hydraulic pressure capacity of pump that is directly driven by driving engine are that the flow during with engine idle is determined.Along with the speed of a motor vehicle increases, the flow of Hydraulic Pump increases gradually, and the hydraulic booster effect also increases gradually.But steering swivel system when high speed in order to improve " road feel " of chaufeur, not unstable when turning to, often require power steering little.
Some steering effort when having adopted method as speed gear thickness to reduce automobile high-speed of existing hydraulic power-assist steering system, but the manufacturing process complexity of this deflector, cost is higher; Electric boosting steering system mainly is made up of torque sensor, car speed sensor, electrical motor, speed reduction gearing and electronic control unit (ECU) etc., when chaufeur turns at the steering dish, motor controller makes electrical motor export the power steering torque of corresponding size and Orientation, thereby produces auxiliary power.When automobile did not turn to, electronic control unit did not send instruction to motor controller, and electrical motor is not worked.Electric boosting steering system also can address this problem preferably, but the relative hydraulic booster system of cost wants high a lot.
The utility model content
The purpose of this utility model is to provide a kind of device that reduces the effect of hydraulic power-assisted steering high servo, guarantee that hydraulic control servo-steering automobile can reduce the hydraulic power-assisted steering effect effectively when running at high speed, improve " road feel " of chaufeur, make turn to sedate, not unstable, seek a kind of device that reduces the effect of high-speed hydraulic servo-steering power-assisted cheaply.
The technical scheme that realizes above-mentioned purpose and take, with fast by pass valve, constituted by piston body, valve body and spring, it is characterized in that valve body one end is provided with the oil pressure input port, the other end is closed end, piston body is housed in the valve body, the both sides of valve body correspondence are provided with oil inlet and oil outlet, between the end of the closed end of valve body and piston body spring are housed, and valve body is provided with step by in the end of oil pressure input port.
Described piston body comprises left piston, right piston, and the piston rod that connects left piston and right piston.
The external diameter of described valve block internal diameter and left piston, right piston matches, and the outer end of right piston peaks at valve body by the step of oil pressure input port.
Described oil pressure input port is coaxial with valve body.
Described left piston vertical section width is greater than the diameter of oil inlet.
The inboard tube wall of described oil inlet and the initial separation of left piston inner end surface are 5mm～10mm.
Described oil outlet is positioned at the middle section of valve body.
Compared with prior art the utlity model has following advantage: by existing hydraulic power-assist steering system has been increased by one with fast by pass valve, when low speed, to not influence of hydraulic power-assisted steering effect, and when galloping, reduce the hydraulic booster effect of hydraulic power-assist steering system, improve " road feel " of chaufeur, make turn to sedate, not unstable; And manufacturing cost is lower.
Description of drawings
Fig. 1 is that the utility model is with the structural representation of fast by pass valve.
Fig. 2 uses the scheme drawing of state for the utility model.
Among the figure: 1-piston body, 101-left piston, the right piston of 102-, 103-piston rod, 2-valve body, 3-spring, the 4-Hydraulic Pump, 5-petrol storage tank, 6-governor valve, 7-speed-changing mechanism, 8-steering control valve, 9-turbine transformer/power-transfer clutch, A-oil inlet, B-oil outlet, C-oil pressure input port, △-initial separation.
Specific embodiments
Below in conjunction with drawings and Examples the utility model is further described, referring to Fig. 1 and Fig. 2, with fast by pass valve, constituted by piston body 1, valve body 2 and spring 3, it is characterized in that, valve body 2 one ends are provided with oil pressure input port C, the other end is closed end, and piston body 1 is housed in the valve body 2, and the both sides of valve body 2 correspondences are provided with oil inlet A and oil outlet B, between one end of the closed end of valve body 2 and piston body 1 spring 3 is housed, valve body 2 is provided with step by in the end of input port C.
Described piston body 1 comprises left piston 101, right piston 102, and the piston rod 103 that connects left piston 101 and right piston 102.
The external diameter of described valve body 2 internal diameters and left piston 101, right piston 102 matches, and the outer end of right piston 102 peaks at valve body 2 by the step of oil pressure input port C.
Described oil pressure input port C is coaxial with valve body 2.
Described left piston 101 vertical section width are greater than the diameter of oil inlet A.
The initial separation △ of the inboard tube wall of described oil inlet A and left piston 101 inner end surfaces is 5mm～10mm.
Described oil outlet B is positioned at the middle section of valve body 2.
Using method of the present utility model is, petrol storage tank 5 delivery ports connect Hydraulic Pump 4 input ports, the delivery port of Hydraulic Pump 4 connects the oil inlet A of valve body 2 and the input port of steering control valve 8, the delivery port of steering control valve 8 connects petrol storage tank 5 input ports, the oil outlet B of valve body 2 connects petrol storage tank 5 input ports, governor valve 6 delivery ports connect oil pressure input port C, and governor valve 6 is installed on the speed-changing mechanism 7, and speed-changing mechanism 7 links to each other with engine crankshaft by turbine transformer/power-transfer clutch 9.
Along with crankshaft rotating speed increases, Hydraulic Pump 4 outlet oil pressure increase, and the hydraulic power-assisted steering effect increases, and corresponding governor valve 6 outlet oil pressure also increase, and act on the thrust on the fast by pass valve 2 right pistons 102 also to increase gradually.In the starting stage, owing to come hydraulic oil A oil duct that one initial separation △ is arranged with fast by pass valve 2 left pistons 101 from Hydraulic Pump, so when crankshaft rotating speed does not reach certain value, inoperative with fast by pass valve 2, need the requirement of bigger power steering when not influencing automobile low speed like this; Further raising along with crankshaft rotating speed, when reaching certain value, act on the elastic force effect that will overcome left side spring 3 with the thrust on the fast by pass valve 2 right pistons 102, make outer the correcting of right piston 102 peak at valve body 2 by the step of oil pressure input port C one end, and left piston 101 to the left oil pressure input port C miles of relative movement reached initial separation △ 8mm, at this moment, A oil duct with fast by pass valve 2 is opened, the steering hydraulic oil that is come out by Hydraulic Pump 4 is via flowing back into petrol storage tank 5 with fast by pass valve 2, the steering oil that flows to steering control valve 8 like this reduces, and the hydraulic power-assisted steering effect reduces relatively.Along with the further increase of crankshaft rotating speed, strengthen via the hydraulic power-assisted steering oil mass that flow back into petrol storage tank 5 with fast by pass valve 2, the hydraulic power-assisted steering effect further reduces, thereby reaches the effect that reduces hydraulic power-assisted steering when high speed.
Embodiment: as shown in Figure 1, for the utility model has set up one with fast by pass valve on the basis of existing hydraulic power-assist steering system, mainly comprise parts such as piston body 1, valve body 2, spring 3, and the hydraulic oil oil inlet A of Hydraulic Pump 4 is to petrol storage tank 5 hydraulic oil oil outlet B, from three oil duct interfaces of the hydraulic fluid pressure input port C of governor valve 6.Piston body 1 is made up of left and right two pistons, left piston 101 is mainly used in controlling the open and close that Hydraulic Pump 4 comes hydraulic oil oil inlet A, and be subjected to spring 3 thrust to the right, right piston 102 mainly bears the thrust left that produces from governor valve 6 oil pressure, and the thrust size and Orientation that spring force and oil pressure produce determines Hydraulic Pump 4 to come the open and close of hydraulic oil oil inlet A.
Accompanying drawing 2 uses the scheme drawing of state for the utility model.Along with crankshaft rotating speed increases, Hydraulic Pump 4 outlet oil pressure increase, and the hydraulic power-assisted steering effect increases, and corresponding governor valve 6 outlet oil pressure also increase, and act on the thrust on the fast by pass valve 2 right pistons 102 also to increase gradually.In the starting stage, because from the inboard tube wall of the hydraulic oil oil inlet A of Hydraulic Pump 4 and left piston 101 inner end surfaces one initial separation △ being arranged with fast by pass valve 2 left pistons 101 is 8mm, so when crankshaft rotating speed does not reach certain value, inoperative with fast by pass valve 2, need the requirement of bigger power steering when not influencing automobile low speed like this; Further raising along with crankshaft rotating speed, when reaching certain value, act on the elastic force effect that will overcome left side spring 3 with the thrust on the fast by pass valve 2 right pistons 102, make left piston 101 to the left miles of relative movement reached initial separation △ 8mm, at this moment, open with the oil inlet A oil duct of fast by pass valve 2, the steering hydraulic oil that is come out by Hydraulic Pump 4 is via flowing back into petrol storage tank 5 with fast by pass valve 2, at this moment the steering oil that flows to steering control valve 8 reduces, and the hydraulic power-assisted steering effect reduces relatively.Along with the further increase of crankshaft rotating speed, strengthen via the hydraulic power-assisted steering oil mass that flow back into petrol storage tank 5 with fast by pass valve 2, the hydraulic power-assisted steering effect further reduces, thereby reaches the effect that reduces hydraulic power-assisted steering when high speed.
A kind of suitable hydraulic power-assisted steering automobile reduce the effect of hydraulic power-assisted steering high servo with fast by pass valve and hydraulic power-assist steering system thereof, when the speed of a motor vehicle reaches certain value, the steering hydraulic oil that is come out by Hydraulic Pump 4 is via flowing back into petrol storage tank 5 with fast by pass valve, and the power steering effect reduces relatively.Along with the further increase of rotating speed, strengthen via the oil mass that turns to that flow back into petrol storage tank 5 with fast by pass valve, the power steering effect further reduces, thereby reaches the effect that reduces the hydraulic power-assisted steering power-assisted when high speed.
Claims (7)
1. with fast by pass valve, constituted by piston body, valve body and spring, it is characterized in that, valve body one end is provided with the oil pressure input port, the other end is closed end, and piston body is housed in the valve body, and the both sides of valve body correspondence are provided with oil inlet and oil outlet, between one end of the closed end of valve body and piston body spring is housed, valve body is provided with step by in the end of input port.
2. according to claim 1ly it is characterized in that with fast by pass valve described piston body comprises left piston, right piston, and the piston rod that connects left piston and right piston.
3. according to claim 1 and 2ly it is characterized in that with fast by pass valve described left piston vertical section width is greater than the diameter of oil inlet.
4. according to claim 1 and 2ly it is characterized in that with fast by pass valve the inboard tube wall of described oil inlet and the initial separation of left piston inner end surface are 5mm～10mm.
5. according to claim 1 and 2ly it is characterized in that with fast by pass valve the external diameter of described valve block internal diameter and left piston, right piston matches, the outer end of right piston peaks at valve body by the step of input port.
6. according to claim 1ly it is characterized in that with fast by pass valve described oil pressure input port is coaxial with valve body.
7. according to claim 1ly it is characterized in that with fast by pass valve described oil outlet is positioned at the middle section of valve body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320190110 CN203142767U (en) | 2013-04-16 | 2013-04-16 | Speed following overflow valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320190110 CN203142767U (en) | 2013-04-16 | 2013-04-16 | Speed following overflow valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203142767U true CN203142767U (en) | 2013-08-21 |
Family
ID=48970315
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320190110 Expired - Fee Related CN203142767U (en) | 2013-04-16 | 2013-04-16 | Speed following overflow valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203142767U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103192875A (en) * | 2013-04-16 | 2013-07-10 | 九江学院 | Speed-following overflow valve and utilization method thereof |
-
2013
- 2013-04-16 CN CN 201320190110 patent/CN203142767U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103192875A (en) * | 2013-04-16 | 2013-07-10 | 九江学院 | Speed-following overflow valve and utilization method thereof |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130821 Termination date: 20140416 |