CN2486371Y - Damping valve of damper for high speed power locomotive oil pressure - Google Patents
Damping valve of damper for high speed power locomotive oil pressure Download PDFInfo
- Publication number
- CN2486371Y CN2486371Y CN 01249271 CN01249271U CN2486371Y CN 2486371 Y CN2486371 Y CN 2486371Y CN 01249271 CN01249271 CN 01249271 CN 01249271 U CN01249271 U CN 01249271U CN 2486371 Y CN2486371 Y CN 2486371Y
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- China
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- oil
- valve
- damping
- damper
- pressure
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- Expired - Fee Related
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Abstract
The utility model is a damping valve of the oil-pressure vibration absorber of high-speed electric locomotives and pertains to oil-pressure vibration absorbers. The utility model is expected to provide a damping valve that provides the optimal damping force at various speeds of high-speed electric locomotives. The type of the damping valve can ensure stability and safety of locomotives during fast traveling and increase the quality and working life of oil-pressure vibration absorbers. The damping valve is characterized in that the utility model consists of a high-speed damping throttle valve, a high-speed damping relief valve, a total-working-condition damping throttle valve and a total-working-condition damping relief valve. All damping valves are placed at the end of the oil cylinder of the oil-pressure vibration absorber and distributed in a circumferential manner. The utility model is mainly used in the oil-pressure vibrator absorber of high-speed electric locomotive so that the damping force of the vibration absorber can eliminate vibration of locomotives.
Description
Technical field:
The utility model relates to a kind of electric express locomotive oil-pressure damper damper valve, belongs to the oil-pressure damper class.
Background technology:
Damper valve is to place in the oil-pressure damper of electric express locomotive or other highspeed rail vehicles, makes shock absorber produce the important component that dumping force is eliminated vibration of rolling stock.
Present shock absorber, stretching or compressing under the operating mode, the cutoff port and the vibration damping valve opening that have only a fixed diameter mostly, can only satisfy rolling stock requirement to pore size when low speed, middling speed operation, and the requirement can not satisfy high-speed cruising the time, vibration velocity is multiplied during high-speed cruising, oil mass by the vibration damping valve opening also is multiplied, because of not strengthening in the aperture, cause the oil cylinder internal pressure excessive, form rigid shock, influence rolling stock traveling comfort, safety, cause the breakage of shock absorber, leakage of oil.Though also some oil-pressure damper has been designed to a plurality of damper valves at present, but not by of the different requirements of basic, normal, high speed operation phase to damper valve sectional area size, come automatic guidance vibration damping valve opening sectional area size, because if vibration damping valve opening sectional area is excessive when low speed, middling speed, make the oil cylinder internal pressure excessive, cause the moment rigid shock again easily, influence highspeed rail vehicle traveling comfort and safety, even can cause the damage and the leakage of oil of shock absorber.
Summary of the invention:
The purpose of this utility model is to provide a kind of electric express locomotive can both reach the damper valve of optimum damping power in the friction speed operation phase; this damper valve can be guaranteed stationarity and the safety of locomotive when high-speed cruising, improves the quality and the life-span of oil-pressure damper.
For achieving the above object, technical solution of the present utility model is: in the auto shock absorber end, four damper valves that function is different are set, to coordinate to finish whole vibration-damping functions.
Of the present utility model being characterised in that: it is by high speed restrictions damper valve 5, high speed off-load damper valve 6, and full operating mode throttling damper valve 12 and full operating mode off-load damper valve 8 are formed, and all damper valves all place in the oil-pressure damper oil storage cylinder end 1, and are circumferential and distribute.
The utility model has the advantages that: 1, rational in infrastructure; be used in the electric express locomotive oil-pressure damper; can guarantee that locomotive moves in any speed stage; all can obtain optimum damping power; the stationarity and the safety of locomotive operation have been guaranteed, the quality and the life-span of also having improved oil-pressure damper greatly simultaneously.2, the dumping force of damper valve can be adjusted to the scope that needs under the condition of not dismantling shock absorber.
Description of drawings:
Fig. 1 is an electric express locomotive oil-pressure damper structural representation, wherein, and 1-auto shock absorber end, 12-damper valve, 17-upper cylinder, 18-piston, 19-oil storage cylinder, 20-piston rod, 21-Connecting jont, 22-check (non-return) valve, oil cylinder under the 23-, 24-bottom check (non-return) valve.
Fig. 2 is a high speed damper valve structural representation, wherein, 1-auto shock absorber end, 2-transfers spring nut, 3-throttling damper valve holddown spring, 4-throttling damper valve sliding sleeve, 5-high speed restrictions damper valve, 6-high speed off-load damper valve, 7-high speed damper valve holddown spring.
Fig. 3 is full operating mode damper valve structural representation, wherein, the full operating mode off-load of 8-damper valve, 9-off-load damper valve compresses sliding sleeve, 10-off-load damper valve holddown spring, 11-high speed packing ring, the full operating mode throttling of 12-damper valve.
Fig. 4 is the distribution schematic diagram of damper valve in the oil storage cylinder end, wherein, and 5-high speed restrictions damper valve, 6-high speed off-load damper valve, the full operating mode throttling of 12-damper valve, the full operating mode off-load of 8-damper valve.
The specific embodiment:
Referring to Fig. 1 and Fig. 2, when locomotive vibration, piston 18 moves up and down in oil cylinder 23, when shock absorber stretched, piston upwards moved in oil cylinder 23, and check (non-return) valve 22 cuts out, bottom check (non-return) valve 24 is opened, the upper cylinder internal pressure increases, and that backs down damper valve 12 compresses sliding sleeve 4, and oil flows to oil storage cylinder 19, simultaneously, following oil cylinder 23 causes negative pressure to make oil storage cylinder 19 interior oil back down bottom check (non-return) valve 24 because of volume strengthens, flow to oil cylinder 23 down, otherwise, when shock absorber compresses, piston 18 moves down, and bottom check (non-return) valve 24 cuts out, and the oil in the following oil cylinder 23 backs down check (non-return) valve 22 and flows to oil cylinder 17, because of oil cylinder inner piston rod 20 lengthenings, volume strengthens, so the volume of whole cylinder diminishes, enters oil storage cylinder 19 so surplus oil backs down the clamping sleeve 4 of damper valve 13.
Referring to Figure 24, when rolling stock is the general speed operation, because the shock absorber vibration velocity is little, the oil pressure that produces can only be opened full operating mode throttling damper valve 12 and full operating mode off-load damper valve 8, this moment, high speed restrictions damper valve 5 and high speed off-load damper valve 6 were in running order, so the shock absorber oil in-cylinder pressure can reach optimum damping power; When rolling stock during at high-speed cruising, because the vibration velocity of shock absorber is multiplied, still lean on the aperture of full operating mode throttling damper valve 12 and full operating mode off-load damper valve 8 this moment, can not satisfy by double oily flow, therefore, the shock absorber oil in-cylinder pressure strengthens, back down high speed restrictions damper valve 5 and high speed off-load damper valve 6, the interior oil pressure of oil cylinder is still remained in the allowed band, and the sectional area in hole doubles, this has just guaranteed that the shock absorber oil in-cylinder pressure remains within the specific limits, keep best damping power, simultaneously, also avoid producing the possibility of rigid shock, guaranteed locomotive operation stationarity and safety.
Claims (1)
1, a kind of electric express locomotive oil-pressure damper damper valve, it is characterized in that: it is by high speed restrictions damper valve (5), high speed off-load damper valve (6), full operating mode throttling damper valve (12) and full operating mode off-load damper valve (8) are formed, all damper valves all place in the oil-pressure damper oil storage cylinder end (1), and are the circumferential distribution.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01249271 CN2486371Y (en) | 2001-07-11 | 2001-07-11 | Damping valve of damper for high speed power locomotive oil pressure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01249271 CN2486371Y (en) | 2001-07-11 | 2001-07-11 | Damping valve of damper for high speed power locomotive oil pressure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2486371Y true CN2486371Y (en) | 2002-04-17 |
Family
ID=33659719
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 01249271 Expired - Fee Related CN2486371Y (en) | 2001-07-11 | 2001-07-11 | Damping valve of damper for high speed power locomotive oil pressure |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2486371Y (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104912992A (en) * | 2014-03-14 | 2015-09-16 | 长春孔辉汽车科技股份有限公司 | Membrane-type amplitude-correlation vibration reduction device |
-
2001
- 2001-07-11 CN CN 01249271 patent/CN2486371Y/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104912992A (en) * | 2014-03-14 | 2015-09-16 | 长春孔辉汽车科技股份有限公司 | Membrane-type amplitude-correlation vibration reduction device |
| CN104912992B (en) * | 2014-03-14 | 2017-03-15 | 长春孔辉汽车科技股份有限公司 | Membrane type amplitude correlation vibroshock |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |