CN205244515U - Diesel engine is two -stage voltage limiting valve for high pressure common rail - Google Patents
Diesel engine is two -stage voltage limiting valve for high pressure common rail Download PDFInfo
- Publication number
- CN205244515U CN205244515U CN201521122346.5U CN201521122346U CN205244515U CN 205244515 U CN205244515 U CN 205244515U CN 201521122346 U CN201521122346 U CN 201521122346U CN 205244515 U CN205244515 U CN 205244515U
- Authority
- CN
- China
- Prior art keywords
- pressure
- valve
- oil
- spool
- valve body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn - After Issue
Links
Landscapes
- Safety Valves (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The utility model discloses a diesel engine is two -stage voltage limiting valve for high pressure common rail, including valve body and a step valve and the two -stage valve of setting on the valve body. The control of pressing the rail when this voltage limiting valve is used for diesel engine work trouble realizes maintaining low pressure after the voltage limiting valve is opened, with low operating mode operation, reduce cost of maintenance after messenger's diesel engine trouble.
Description
Technical field
The utility model relates to fuel common-rail technical field, is specially a kind of diesel engine high-pressure co-rail two-stage pressure limiting valve.
Background technology
High pressure co-rail system is the main development direction of diesel engine in recent years, high-pressure common rail can be realized high injection pressure, controlled injection timing, the more difficult function that maybe cannot realize of traditional fuel injection system such as multi-injection, has greatly improved to Exhaust Control for Diesel Engine and fuel economy.
When Design of High Pressure Common Rail Diesel Engine operation irregularity, can cause rail pressure wink liter, in the time exceeding ECU regulating power or ECU and break down, diesel engine will be out of control, then causes many potential safety hazards. Therefore diesel engine will be opened safety valve after rail pressure wink rises, and rail pressure is maintained to a lower level, reduces the generation of security incident.
Summary of the invention
The purpose of this utility model is to provide a kind of diesel engine high-pressure co-rail two-stage pressure limiting valve, and the maximum pressure allowing for restriction system can make diesel engine enter to fall the fault mode operation of power after pressure limiting valve is opened, and ensures security of system.
Diesel engine high-pressure co-rail described in the utility model two-stage pressure limiting valve, comprise valve body and be vertically arranged in one-step valve and the horizontally disposed secondary valve on valve body on valve body, the first spool bore that vertically offers oil input channel and be communicated with oil input channel on described valve body, described one-step valve comprises oil connection, the first spool, pressure spring and pressure spring seat, described oil connection hollow, it is arranged on valve body, make to form between described oil connection and valve body a chamber, described the first spool is engaged in the first spool bore of valve body, the seat surface fitted seal of the front end conical surface of the first spool and the first spool bore front end, the rear end of described the first spool is arranged on pressure spring seat, described pressure spring is arranged in the centre bore of oil connection, and its two ends are against respectively on oil connection and pressure spring seat, described secondary valve comprises valve seat, rear valve gap, the second spool, pressure-stabilizing spring and pressure-stabilizing spring seat, described valve seat being arranged in valve body in horizontal direction, the center of valve seat is provided with the second spool bore, described the second spool bore is communicated with the first spool bore by the intercommunicating pore on valve body, described the second spool is engaged in the second spool bore of valve seat, the front end oil-in fitted seal of the front end conical surface of the second spool and the second spool bore, the rear end of described the second spool is arranged on pressure-stabilizing spring seat, described rear valve gap is arranged on valve body, its front end props up described valve seat, described pressure-stabilizing spring is positioned at rear valve gap, its two ends are against respectively on rear valve gap and pressure-stabilizing spring seat, on the sidewall of described valve seat, be provided with the first oil-through hole, described the first oil-through hole is communicated with the second spool bore, described valve body is provided with the first oil duct being communicated with the first oil-through hole, the fluid that makes to enter in the second spool bore drains in the chamber between oil connection and valve body through the first oil-through hole and the first oil duct, on described rear valve gap sidewall, be provided with the second oil-through hole, described valve body is provided with the second oil duct being communicated with the second oil-through hole, the fluid being flowed out backward by the fit clearance of the second spool periphery and the second spool bore is also drained in the chamber between oil connection and valve body by described the second oil-through hole and the second oil duct.
Preferably, be arranged with collar and bell tap in described valve body lower portion.
Preferably, on the centre bore bottom hole wall of described oil connection, there is enlarging groove.
Preferably, in described rear valve gap, be provided with spacing mandril, this spacing mandril front end coordinates with pressure-stabilizing spring seat, capable spacing to shift-in after pressure-stabilizing spring seat.
Preferably, the conical surface opening diameter of described valve seat front end oil-in is slightly larger than the forward end seal conical surface diameter of the second spool.
Preferably, described pressure-stabilizing spring is enclosed within on spacing mandril, and described spacing mandril is multidiameter, and described rear valve gap endoporus is shoulder hole.
Preferably, described oil connection is connected with valve body by screw thread, and forms flat seal by the outer rim lower surface of oil connection and the upper surface of valve body.
Preferably, described rear valve gap is connected with valve body by screw thread, and at screw thread place sealant sealing.
Preferably, in described oil connection and rear valve gap, correspondence is provided with pressure spring pad and pressure-stabilizing spring pad respectively.
Preferably, the rear end face of the tail end face of described the second spool and pressure-stabilizing spring seat is sphere.
Diesel engine high-pressure co-rail described in the utility model two-stage pressure limiting valve, can arrange the opening pressure of system, prevents diesel engine pressure limit, ensures the safety of diesel engine. After diesel engine rail pressure is out of control, can ensure that diesel engine enters fault mode work lower maintaining under pressure, walk lamely to maintenace point, reduce engine maintenance cost. And this pressure limiting valve to unload current-carrying capacity adaptability extremely strong, can meet the instructions for use of various different diesel engines.
Brief description of the drawings
Fig. 1 is cutaway view of the present utility model;
Fig. 2 is the cutaway view of oil connection in the utility model;
Fig. 3 is the upward view of oil connection in the utility model;
Fig. 4 is the cutaway view of valve body in the utility model;
Fig. 5 is the partial enlarged drawing at A place in Fig. 1;
Fig. 6 is the partial enlarged drawing at B place in Fig. 1;
Fig. 7 is the partial enlarged drawing at the second seal spool place in the utility model;
Fig. 8 is the partial enlarged drawing of rear valve gap in the utility model.
Detailed description of the invention
Below in conjunction with drawings and Examples, the utility model is described in further detail, and following examples only, for explaining the utility model, do not form the restriction to the utility model protection domain.
The two-stage pressure limiting valve of diesel engine high-pressure co-rail as shown in Figure 1, comprises the one-step valve and the horizontally disposed secondary valve on valve body 1 that are vertically arranged on valve body 1. One-step valve comprises oil connection 2, the first spool 3, pressure spring 4 and pressure spring seat 5, and secondary valve comprises valve seat 7, rear valve gap 8, the second spool 9, pressure-stabilizing spring 10, pressure-stabilizing spring seat 11 and spacing mandril 12.
Referring to Fig. 4, the bottom of described valve body 1 has the cylinder 101 that rail pressure accumulation chamber connects together, the first spool bore that vertically offers oil input channel 102 and be communicated with oil input channel on valve body 1. On valve body lower portion cylinder, be arranged with collar 14 and bell tap 15, and in this enforcement, under valve body, square thread and collar screw thread all adopt left hand thread, this pressure limiting valve is connected on common rail pressure accumulation chamber by described collar 14 and bell tap 15, can rotate as required any direction again threaded together female connector fix.
Referring to Fig. 2, Fig. 3, described oil connection 2 is arranged in the installing hole 103 on valve body top by screw thread, and outer rim lower surface 202 by oil connection forms flat seal with the upper surface 104 of valve body, makes to form between described oil connection and valve body a chamber. When fuel oil is full of oil connection and valve body gap V1, pressure has dropped to very lowly, ensures the roughness control of oil connection outer rim lower surface and valve body upper surface within the specific limits, to realize fuel low-pressure sealing. Differential hardening processing is done in described oil connection lower surface 203, improves its service life.
Referring to Fig. 5, described the first spool 3 is engaged in the first spool bore of valve body, the first spool and valve body are couple pair relationhip, seat surface 105 fitted seal of the front end conical surface of the first spool and the first spool bore front end, and the rear end of described the first spool 3 is arranged on pressure spring seat 4.
Described pressure spring 4 is arranged in the centre bore of oil connection 2, and its two ends are against respectively on the pressure spring pad 6 in pressure spring seat 5 and oil connection centre bore, carry out regulating spring pretightning force by the pressure spring pad of selecting different-thickness. Pressure spring seat locating surface 501 apart from oil connection lower surface distance L EssT.LTssT.LT 1mm, the first spool open after oil connection lower surface play position-limiting action.
Referring to Fig. 6, being arranged in valve body 1 of described valve seat 7 along continuous straight runs, the center of valve seat is provided with the second spool bore, and described the second spool bore is by intercommunicating pore 106 and the first spool bore radial communication of side direction on valve body.
Described the second spool 9 is engaged in the second spool bore of valve seat, and the second spool 9 is couple pair relationhip with valve seat. The front end oil-in fitted seal of the front end conical surface of the second spool and the second spool bore, the rear end of the second spool is arranged on pressure-stabilizing spring seat.
In order to save manufacturing cost, the first spool in the present embodiment is identical with the physical dimension of the second spool.
For ensureing that pressure limiting valve can withstand shocks, the rear end face 1101 of the tail end face of described the second spool 901 and pressure-stabilizing spring seat is designed to the sphere of large radius.
Described rear valve gap 8 is arranged on by screw thread on the installing hole 109 of valve body sidepiece, described valve seat is compressed, when fuel oil is full of rear valve gap 8 with valve body 1 gap V2 pressure will arrive very low, by sealing with happy safe glue at screw thread place.
Referring to Fig. 7, because the valve seat front end oil-in conical surface 701 and the second spool conical surface 902 parallel-segment distance L 1 are still subject to the pressure influence of size between high-pressure side and low-pressure end after the second spool is opened, for eliminating this impact, make secondary valve can better stablize rail pressure, need reduce by two conical surface parallel-segment length, therefore the conical surface opening diameter D1 of valve seat front end oil-in is slightly larger than and approaches the forward end seal conical surface diameter D2 of the second spool in the scope allowing at processing conditions as far as possible as far as possible.
On the sidewall of described valve seat 7, be provided with the first oil-through hole 702, described the first oil-through hole is communicated with the second spool bore, described valve body is provided with the first oil duct 107 being communicated with the first oil-through hole, the fluid that makes to enter in the second spool bore drains in the chamber between oil connection and valve body through the first oil-through hole 702 and the first oil duct 107, on described rear valve gap 8 sidewalls, be provided with the second oil-through hole 801, described valve body is provided with the second oil duct 108 being communicated with the second oil-through hole, the fluid being flowed out backward by the fit clearance of the second spool periphery and the second spool bore is also drained in the chamber between oil connection and valve body by described the second oil-through hole 801 and the second oil duct 108. for fear of producing restriction effect herein, on the hole wall of the centre bore bottom of oil connection, symmetry offers two enlarging grooves 201.
In described rear valve gap 8, be provided with spacing mandril 12, this spacing mandril front end coordinates with pressure-stabilizing spring seat, and spacing mandril and pressure-stabilizing spring base rear end distance L EssT.LTssT.LT 1mm are capable spacing to shift-in after pressure-stabilizing spring seat.
Described pressure-stabilizing spring 10 is sleeved on spacing mandril 12, and its two ends are against respectively on the pressure-stabilizing spring pad 13 in pressure-stabilizing spring seat and rear valve gap.
Referring to Fig. 8, described spacing mandril 12 is multidiameter 1201, and described rear valve gap 8 endoporus are shoulder hole 802, thereby avoids the wearing and tearing of in the time that secondary valve is worked pressure-stabilizing spring 10 and spacing mandril and rear valve cover chamber.
The operation principle of above-mentioned two-stage pressure limiting valve is: in the time that diesel engine work is normal, pressure accumulation cavity pressure can not be greater than pressure limiting valve opening pressure. Now fuel oil enters to the first spool 3 belows by the oil input channel 102 of pressure limiting valve lower end, and the active force of pressure spring 4 acts on the first spool, makes its front end conical surface and the first spool bore seat surface 105 form seal band fuel oil is realized to sealing.
In the time that diesel engine work is abnormal, pressure wink liter, when rail pressure is during higher than opening pressure, the first spool 3 of one-step valve overcomes pressure spring 4 active forces and upwardly opens, pressure spring seat 5 goes upward to rapidly spacing place, because spool guiding area is greater than sealing surface several times, therefore spool is still held open state under lower fuel pressure always. After one-step valve is opened, because fuel pressure is far above secondary valve opening pressure, will open fast so locate spool, secondary valve is started working, and spacing mandril 12 is clashed into rapidly in pressure-stabilizing spring seat 11 rear ends, reaches spacing position. After unlatching, in the second spool bore of fuel admission valve seat, flow in the chamber between oil connection and valve body by the first oil duct 107 on the first oil-through hole 702 and valve body on valve seat, then lead to fuel tank through the oil road on oil connection top, pressure is reduced to rapidly secondary valve opening pressure, and the second spool 9 makes rail pressure remain on diesel engine desired level by pressure-stabilizing spring 10 restoring forces. The fuel oil of the clearance leakage of the second spool 9 and the second spool bore flows to oil connection place via the second oil-through hole 801 and the second oil duct 108, leads in the lump fuel tank with the fuel oil of the fuel oil of the first oil duct and the clearance leakage of the first spool and the first spool bore.
Claims (10)
1. a diesel engine high-pressure co-rail two-stage pressure limiting valve, it is characterized in that: comprise valve body and be vertically arranged in one-step valve and the horizontally disposed secondary valve on valve body on valve body, the first spool bore that vertically offers oil input channel and be communicated with oil input channel on described valve body;
Described one-step valve comprises oil connection, the first spool, pressure spring and pressure spring seat, described oil connection hollow, it is arranged on valve body, make to form between described oil connection and valve body a chamber, described the first spool is engaged in the first spool bore of valve body, the seat surface fitted seal of the front end conical surface of the first spool and the first spool bore front end, the rear end of described the first spool is arranged on pressure spring seat, described pressure spring is arranged in the centre bore of oil connection, and its two ends are against respectively on oil connection and pressure spring seat;
Described secondary valve comprises valve seat, rear valve gap, the second spool, pressure-stabilizing spring and pressure-stabilizing spring seat, described valve seat being arranged in valve body in horizontal direction, the center of valve seat is provided with the second spool bore, described the second spool bore is communicated with the first spool bore by the intercommunicating pore on valve body, described the second spool is engaged in the second spool bore of valve seat, the front end oil-in fitted seal of the front end conical surface of the second spool and the second spool bore, the rear end of described the second spool is arranged on pressure-stabilizing spring seat, described rear valve gap is arranged on valve body, its front end props up described valve seat, described pressure-stabilizing spring is positioned at rear valve gap, its two ends are against respectively on rear valve gap and pressure-stabilizing spring seat,
On the sidewall of described valve seat, be provided with the first oil-through hole, described the first oil-through hole is communicated with the second spool bore, described valve body is provided with the first oil duct being communicated with the first oil-through hole, the fluid that makes to enter in the second spool bore drains in the chamber between oil connection and valve body through the first oil-through hole and the first oil duct, on described rear valve gap sidewall, be provided with the second oil-through hole, described valve body is provided with the second oil duct being communicated with the second oil-through hole, the fluid being flowed out backward by the fit clearance of the second spool periphery and the second spool bore is also drained in the chamber between oil connection and valve body by described the second oil-through hole and the second oil duct.
2. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, is characterized in that: be arranged with collar and bell tap in described valve body lower portion.
3. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, is characterized in that: on the centre bore bottom hole wall of described oil connection, have enlarging groove.
4. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, is characterized in that: in described rear valve gap, be provided with spacing mandril, this spacing mandril front end coordinates with pressure-stabilizing spring seat, capable spacing to shift-in after pressure-stabilizing spring seat.
5. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, is characterized in that: the conical surface opening diameter of described valve seat front end oil-in is slightly larger than the forward end seal conical surface diameter of the second spool.
6. diesel engine high-pressure co-rail according to claim 4 two-stage pressure limiting valve, is characterized in that: described pressure-stabilizing spring is enclosed within on spacing mandril, described spacing mandril is multidiameter, and described rear valve gap endoporus is shoulder hole.
7. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, is characterized in that: described oil connection is connected with valve body by screw thread, and forms flat seal by the outer rim lower surface of oil connection and the upper surface of valve body.
8. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, is characterized in that: described rear valve gap is connected with valve body by screw thread, and at screw thread place sealant sealing.
9. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, is characterized in that: in described oil connection and rear valve gap, correspondence is provided with pressure spring pad and pressure-stabilizing spring pad respectively.
10. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, is characterized in that: the rear end face of the tail end face of described the second spool and pressure-stabilizing spring seat is sphere.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521122346.5U CN205244515U (en) | 2015-12-31 | 2015-12-31 | Diesel engine is two -stage voltage limiting valve for high pressure common rail |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521122346.5U CN205244515U (en) | 2015-12-31 | 2015-12-31 | Diesel engine is two -stage voltage limiting valve for high pressure common rail |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205244515U true CN205244515U (en) | 2016-05-18 |
Family
ID=55943594
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201521122346.5U Withdrawn - After Issue CN205244515U (en) | 2015-12-31 | 2015-12-31 | Diesel engine is two -stage voltage limiting valve for high pressure common rail |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205244515U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443816A (en) * | 2015-12-31 | 2016-03-30 | 重庆红江机械有限责任公司 | Two-stage pressure limiting valve for diesel engine high pressure common rail |
| CN112728168A (en) * | 2021-01-14 | 2021-04-30 | 中国航发长春控制科技有限公司 | Integrated forward high-sealing one-way valve |
-
2015
- 2015-12-31 CN CN201521122346.5U patent/CN205244515U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443816A (en) * | 2015-12-31 | 2016-03-30 | 重庆红江机械有限责任公司 | Two-stage pressure limiting valve for diesel engine high pressure common rail |
| CN105443816B (en) * | 2015-12-31 | 2017-11-14 | 重庆红江机械有限责任公司 | Diesel engine high-pressure co-rail two-stage pressure limiting valve |
| CN112728168A (en) * | 2021-01-14 | 2021-04-30 | 中国航发长春控制科技有限公司 | Integrated forward high-sealing one-way valve |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102444637B (en) | Plug-in overflow valve | |
| CN103090070B (en) | Piloted reducer | |
| CN203009431U (en) | Cushion valve for excavator motor | |
| CN104314725A (en) | Middle hole pressure storage static leakage-free oil sprayer | |
| CN205244515U (en) | Diesel engine is two -stage voltage limiting valve for high pressure common rail | |
| CN101865062A (en) | Constant pressure oil outlet valve | |
| CN205278474U (en) | Pressurized construction of overflow valve | |
| CN103470572B (en) | Hydraulic lock assembly and the bidirectional hydraulic lock with above-mentioned hydraulic lock assembly | |
| CN101949397A (en) | Balanced valve bank of derricking cylinder system | |
| CN205371160U (en) | Pressure boost overflow valve | |
| CN103089728A (en) | Differential type pilot overflow valve | |
| CN105443816A (en) | Two-stage pressure limiting valve for diesel engine high pressure common rail | |
| CN206092583U (en) | Oily relief valve is mended to compact | |
| CN102454650A (en) | Hydraulic differential pilot opening mechanism | |
| CN208950751U (en) | A kind of fuel injector and fuel injection system | |
| CN204140531U (en) | Relief valve | |
| CN103277548B (en) | A kind of common rail pipe protection valve | |
| CN103122881A (en) | Pilot reducing valve | |
| CN109209712A (en) | A kind of fuel injector and fuel injection system | |
| CN204113790U (en) | Relief valve | |
| CN103727306A (en) | Pressure reducer | |
| CN201786790U (en) | Overflow valve for excavator | |
| CN202560417U (en) | Constant pressure fuel outlet valve | |
| CN203309245U (en) | Common rail pipe protection valve | |
| CN201687626U (en) | Isobaric oil outlet valve |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20160518 Effective date of abandoning: 20171114 |
|
| AV01 | Patent right actively abandoned |