CN105443816B - Diesel engine high-pressure co-rail two-stage pressure limiting valve - Google Patents
Diesel engine high-pressure co-rail two-stage pressure limiting valve Download PDFInfo
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- CN105443816B CN105443816B CN201511013835.1A CN201511013835A CN105443816B CN 105443816 B CN105443816 B CN 105443816B CN 201511013835 A CN201511013835 A CN 201511013835A CN 105443816 B CN105443816 B CN 105443816B
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- Prior art keywords
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- oil
- valve body
- diesel engine
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0473—Multiple-way safety valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0049—Combined valve units, e.g. for controlling pumping chamber and injection valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/164—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side and remaining closed after return of the normal pressure
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Safety Valves (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention discloses a kind of diesel engine high-pressure co-rail two-stage pressure limiting valve, including valve body and the one-step valve and secondary valve that are arranged on valve body.Control when this pressure limiting valve is used for diesel engine job failure to rail pressure, realize that pressure limiting valve maintains low pressure after opening, run after making diesel engine fault with low operating mode, reduce maintenance cost.
Description
Technical field
The present invention relates to fuel common-rail technical field, 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 direction of development of diesel engine in recent years, and high-pressure common rail can realize high injection pressure, can
The control conventional fuel oil spraying system such as injection timing, multi-injection is more difficult or the function that can not realize, to Exhaust Control for Diesel Engine and
Fuel economy has greatly improved.
During Design of High Pressure Common Rail Diesel Engine operation irregularity, rail pressure wink liter can be caused, when beyond ECU regulating powers or ECU generation events
During barrier, diesel engine will be out of control, then triggers many potential safety hazards.Therefore diesel engine opens safety valve after being risen in rail pressure wink,
And rail pressure is maintained into a relatively low level, reduce the generation of security incident.
The content of the invention
It is an object of the invention to provide a kind of diesel engine high-pressure co-rail two-stage pressure limiting valve, for limiting system permission
Maximum pressure, diesel engine can be made to enter the fault mode operation of drop power after pressure limiting valve unlatching, ensure system safety.
Diesel engine high-pressure co-rail of the present invention two-stage pressure limiting valve, including valve body and be arranged vertically on valve body one
Step valve and the secondary valve being arranged horizontally on valve body, oil input channel and and oil-feed are vertically offered on the valve body
First spool bore of road connection；The one-step valve includes oil connection, the first valve element, pressure spring and pressure spring seat, described
Oil connection is hollow, and it is arranged on valve body, makes to form a chamber between the oil connection and valve body, and first valve element coordinates
In the first spool bore of valve body, the seat surface fitted seal of the front end conical surface of the first valve element and the first spool bore front end, described
The rear end of one valve element is arranged on pressure spring seat, and the pressure spring is located in the centre bore of oil connection, its both ends difference
It is against on oil connection and pressure spring seat；The secondary valve includes valve seat, rear bonnet, the second valve element, pressure-stabilizing spring and voltage stabilizing
Spring base, the valve seat being arranged in valve body in horizontal direction, the center of valve seat is provided with the second spool bore, second valve element
Hole is connected by the intercommunicating pore on valve body with the first spool bore, and second valve element coordinates in the second spool bore of valve seat, the
The front end conical surface of two valve elements and the front end oil inlet fitted seal of the second spool bore, the rear end of second valve element are arranged on voltage stabilizing
On spring base, the rear bonnet is arranged on valve body, and its front end props up the valve seat, and the pressure-stabilizing spring is located at rear bonnet
Interior, its both ends is against on rear bonnet and pressure-stabilizing spring seat respectively；It is provided with the first oil-through hole in the side wall of the valve seat, described
One oil-through hole connects with the second spool bore, and the valve body is provided with the first oil duct connected with the first oil-through hole, makes to enter second
Fluid in spool bore is drained into the chamber between oil connection and valve body through the first oil-through hole and the first oil duct, in the rear bonnet
Side wall is provided with the second oil-through hole, and the valve body is provided with the second oil duct connected with the second oil-through hole, made outside by the second valve element
The fluid that the fit clearance of week and the second spool bore flows out backward also drains into oil pipe by second oil-through hole and the second oil duct
In chamber between joint and valve body.
Preferably, collar and bell tap are arranged with the valve body lower portion.
Preferably, there is enlarging groove on the centre bore bottom hole wall of the oil connection.
Preferably, spacing mandril is provided with bonnet in the rear, the spacing mandril front end coordinates with pressure-stabilizing spring seat, right
It is spacing that row is moved into after pressure-stabilizing spring seat.
Preferably, the conical surface opening diameter of valve seat front end oil inlet is straight slightly larger than the forward end seal conical surface of the second valve element
Footpath.
Preferably, the pressure-stabilizing spring is enclosed on spacing mandril, and the spacing mandril is multi-diameter shaft, the rear bonnet endoporus
For shoulder hole.
Preferably, the oil connection is connected by screw thread with valve body, and passes through the outer rim lower surface of oil connection and valve
The upper surface of body forms flat seal.
Preferably, the rear bonnet is connected by screw thread with valve body, and sealant sealing is used at screw thread.
Preferably, pressure spring pad and pressure-stabilizing spring pad are correspondingly provided with respectively in the oil connection and rear bonnet
Piece.
Preferably, the rear end face of the tail end face of second valve element and pressure-stabilizing spring seat is sphere.
Diesel engine high-pressure co-rail of the present invention two-stage pressure limiting valve, the Opening pressure of system can be set, prevent diesel oil
Machine pressure limit, ensure the safety of diesel engine.After diesel engine rail pressure is out of control, it is ensured that diesel engine enters under relatively low maintenance pressure
Enter fault mode work, walk lamely to maintenace point, reduce engine maintenance cost.And the relieving flowing volume adaptability pole of this pressure limiting valve
By force, the requirement of various different diesel engines can be met.
Brief description of the drawings
Fig. 1 is the sectional view of the present invention；
Fig. 2 is the sectional view of oil connection in the present invention；
Fig. 3 is the upward view of oil connection in the present invention；
Fig. 4 is the sectional view of valve body in the present invention；
Fig. 5 is the partial enlarged drawing at A in Fig. 1；
Fig. 6 is the partial enlarged drawing at B in Fig. 1；
Fig. 7 is the partial enlarged drawing at the second seal spool in the present invention；
Fig. 8 is the partial enlarged drawing of rear bonnet in the present invention.
Embodiment
The present invention is further elaborated with reference to the accompanying drawings and examples, and following examples are only used for explaining this
Invention, is not intended to limit the scope of the present invention..
Diesel engine high-pressure co-rail as shown in Figure 1 two-stage pressure limiting valve, including the one-step valve being arranged vertically on valve body 1 and
The secondary valve being arranged horizontally on valve body 1.One-step valve includes oil connection 2, the first valve element 3, pressure spring 4 and pressure spring seat
5, secondary valve includes valve seat 7, rear bonnet 8, the second valve element 9, pressure-stabilizing spring 10, pressure-stabilizing spring seat 11 and spacing mandril 12.
Referring to Fig. 4, the bottom of the valve body 1 has the cylinder 101 being connected with common rail pressure accumulation chamber, along vertical on valve body 1
The first spool bore that direction offers oil input channel 102 and connected with oil input channel.Collar 14 is arranged with valve body lower portion cylinder
With bell tap 15, and square thread and collar screw thread use left hand thread under valve body in this implementation, and this pressure limiting valve passes through described
Collar 14 and bell tap 15 are connected on common rail pressure accumulation chamber, can be rotated any direction as needed and are tightened bell tap again and consolidate
It is fixed.
Referring to Fig. 2, Fig. 3, the oil connection 2 passes through oil by being threadably mounted in the mounting hole 103 on valve body top
The outer rim lower surface 202 of pipe joint forms flat seal with the upper surface 104 of valve body, makes to be formed between the oil connection and valve body
One chamber.Fuel oil had dropped down to full of oil connection with pressure during the V1 of valve body gap it is very low, ensure oil connection outer rim lower surface and
The roughness of valve body upper surface controls within the specific limits, to realize that fuel low-pressure seals.Make the oil connection lower surface 203
Differential hardening processing, improves its service life.
Referring to Fig. 5, first valve element 3 coordinates in the first spool bore of valve body, and the first valve element is matched somebody with somebody with valve body for couple
To relation, the fitted seal of seat surface 105 of the front end conical surface of the first valve element and the first spool bore front end, after first valve element 3
End is arranged on pressure spring seat 4.
The pressure spring 4 is located in the centre bore of oil connection 2, and its both ends is against pressure spring seat 5 and oil pipe respectively
On pressure spring pad 6 in connector center hole, initial tension of spring is adjusted by the pressure spring pad from different-thickness.
The locating surface 501 of pressure spring seat is apart from oil connection lower surface distance ＜ 1mm, oil connection lower end after the first valve element is opened
Play position-limiting action in face.
Referring to Fig. 6, the valve seat 7 being arranged in valve body 1 in the horizontal direction, the center of valve seat is provided with the second spool bore,
Second spool bore passes through the spool bore radial communication of intercommunicating pore 106 and first lateral on valve body.
Second valve element 9 coordinates in the second spool bore of valve seat, and the second valve element 9 and valve seat are couple pair relationhip.
The front end conical surface of second valve element and the front end oil inlet fitted seal of the second spool bore, the rear end of the second valve element are arranged on voltage stabilizing bullet
On spring abutment.
In order to save manufacturing cost, the physical dimension of the first valve element and the second valve element in the present embodiment is identical.
To ensure that pressure limiting valve can withstand shocks, after the tail end face 901 and pressure-stabilizing spring seat of second valve element
End face 1101 is designed as the sphere of large radius.
Bonnet 8 is by being threadably mounted on the mounting hole 109 of valve body-side after described, and by the seat compression, fuel oil fills
Pressure will arrive very low during full rear bonnet 8 and 1 gap V2 of valve body, by being sealed at screw thread with happy safe glue.
Referring to Fig. 7, because the valve seat front end oil inlet conical surface 701 and the parallel-segment distance L1 of the second valve element conical surface 902 are in the second valve
Core nevertheless suffers from pressure influence of the size between high-pressure side and low-pressure end after opening, to eliminate this influence so that secondary valve can be more
Good stable rail pressure, need to try one's best reduces the parallel segment length of two conical surfaces, therefore the valve seat front end oil-feed in the range of processing conditions permission
The conical surface opening diameter D1 of mouth is slightly larger than and tried one's best close to the forward end seal conical surface diameter D2 of the second valve element.
The first oil-through hole 702 is provided with the side wall of the valve seat 7, first oil-through hole connects with the second spool bore,
The valve body is provided with the first oil duct 107 connected with the first oil-through hole, and the fluid for making to enter in the second spool bore is through the first mistake
The oil duct 107 of oilhole 702 and first is drained into the chamber between oil connection and valve body, and the side wall of bonnet 8 is provided with second in the rear
Oil-through hole 801, the valve body are provided with the second oil duct 108 connected with the second oil-through hole, made by the second valve element periphery and second
The fluid that the fit clearance of spool bore flows out backward also drains into oil pipe by the oil duct 108 of the second oil-through hole 801 and second and connect
In chamber between head and valve body.It is symmetrical on the centre bore bottom hole wall of oil connection in order to avoid producing restriction effect herein
Offer two enlarging grooves 201.
Spacing mandril 12 is provided with bonnet 8 in the rear, the spacing mandril front end coordinates with pressure-stabilizing spring seat, spacing top
Bar and pressure-stabilizing spring base rear end distance ＜ 1mm, it is spacing to being moved into row after pressure-stabilizing spring seat.
The pressure-stabilizing spring 10 is sleeved on spacing mandril 12, and its both ends is against in pressure-stabilizing spring seat and rear bonnet respectively
On pressure-stabilizing spring pad 13.
Referring to Fig. 8, the spacing mandril 12 is multi-diameter shaft 1201, and the rear endoporus of bonnet 8 is shoulder hole 802, so as to keep away
Exempt from the abrasion of pressure-stabilizing spring 10 and spacing mandril and rear valve cover chamber when secondary valve works.
The operation principle of above-mentioned two-stage pressure limiting valve is：When diesel engine is working properly, pressure accumulation cavity pressure is not more than pressure limiting
Valve opening pressure.Now fuel oil enters to the lower section of the first valve element 3, the work of pressure spring 4 by the oil input channel 102 of pressure limiting valve lower end
Firmly act on the first valve element, its front end conical surface is realized with the first spool bore seat surface 105 formation seal band to fuel oil close
Envelope.
When diesel engine operation irregularity, pressure wink liter, when rail pressure is higher than Opening pressure, 3 grams of the first valve element of one-step valve
Take the active force of pressure spring 4 to upwardly open, pressure spring seat 5 goes upward to rapidly spacing place, is more than sealing because valve element is oriented to area
Face several times, therefore valve element is still always maintained at opening under relatively low fuel pressure.After one-step valve unlatching, because fuel pressure is far high
In two level valve opening pressure, therefore valve element will be opened quickly herein, and secondary valve is started working, and the rear end of pressure-stabilizing spring seat 11 is hit rapidly
Spacing mandril 12, reaches restraining position.After unlatching, in the second spool bore of fuel admission valve seat, pass through the first mistake on valve seat
The first oil duct 107 on oilhole 702 and valve body is flowed into the chamber between oil connection and valve body, then through oil connection top
Oil road leads to fuel tank, and pressure is rapidly reduced to two level valve opening pressure, and the second valve element 9 passes through the restoring force of pressure-stabilizing spring 10
Rail pressure is maintained at horizontal needed for diesel engine.The fuel oil of the clearance leakage of second valve element 9 and the second spool bore is via the second oil-through hole
801 and second oil duct 108 flow at oil connection, fuel oil and the gap of the first valve element and the first spool bore with the first oil duct
The fuel oil of leakage leads to fuel tank in the lump.
Claims (10)
- A kind of 1. diesel engine high-pressure co-rail two-stage pressure limiting valve, it is characterised in that：Including valve body and it is arranged vertically on valve body One-step valve and the secondary valve being arranged horizontally on valve body, oil input channel is vertically offered on the valve body and with entering First spool bore of oil duct connection；The one-step valve includes oil connection, the first valve element, pressure spring and pressure spring seat, and the oil connection is hollow, its On valve body, make to form a chamber between the oil connection and valve body, first valve element coordinates the first valve in valve body In core bore, the seat surface fitted seal of the front end conical surface of the first valve element and the first spool bore front end, the rear end peace of first valve element On pressure spring seat, the pressure spring is located in the centre bore of oil connection, its both ends be against respectively oil connection and On pressure spring seat；The secondary valve includes valve seat, rear bonnet, the second valve element, pressure-stabilizing spring and pressure-stabilizing spring seat, and the valve seat is in level side To be arranged in valve body, the center of valve seat is provided with the second spool bore, second spool bore by the intercommunicating pore on valve body with First spool bore connects, and second valve element coordinates in the second spool bore of valve seat, the front end conical surface of the second valve element and second The front end oil inlet fitted seal of spool bore, the rear end of second valve element are arranged on pressure-stabilizing spring seat, the rear bonnet peace On valve body, its front end props up the valve seat, and the pressure-stabilizing spring is located in rear bonnet, and its both ends is against rear bonnet respectively On pressure-stabilizing spring seat；The first oil-through hole is provided with the side wall of the valve seat, first oil-through hole connects with the second spool bore, the valve body The first oil duct connected with the first oil-through hole is provided with, the fluid for making to enter in the second spool bore is through the first oil-through hole and the first oil Road is drained into the chamber between oil connection and valve body, and bonnet side wall is provided with the second oil-through hole in the rear, is set on the valve body There is the second oil duct connected with the second oil-through hole, make what the fit clearance by the second valve element periphery and the second spool bore flowed out backward Fluid is also drained into the chamber between oil connection and valve body by 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, it is characterised in that：In the valve body lower portion It is arranged with collar and bell tap.
- 3. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, it is characterised in that：The oil connection There is enlarging groove on the hole wall of centre bore bottom.
- 4. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, it is characterised in that：In the rear in bonnet Spacing mandril is provided with, the spacing mandril front end coordinates with pressure-stabilizing spring seat, spacing to being moved into row after pressure-stabilizing spring seat.
- 5. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, it is characterised in that：The valve seat front end is entered The conical surface opening diameter of hydraulic fluid port is slightly larger than the forward end seal conical surface diameter of the second valve element.
- 6. diesel engine high-pressure co-rail according to claim 4 two-stage pressure limiting valve, it is characterised in that：The pressure-stabilizing spring set On spacing mandril, the spacing mandril is multi-diameter shaft, and the rear bonnet endoporus is shoulder hole.
- 7. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, it is characterised in that：The oil connection leads to Cross screw thread to be connected with valve body, and flat seal is formed 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, it is characterised in that：Bonnet passes through after described Screw thread is connected with valve body, and sealant sealing is used at screw thread.
- 9. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, it is characterised in that：In the oil connection With pressure spring pad and pressure-stabilizing spring pad are correspondingly provided with rear bonnet respectively.
- 10. diesel engine high-pressure co-rail according to claim 1 two-stage pressure limiting valve, it is characterised in that：Second valve element Tail end face and the rear end face of pressure-stabilizing spring seat be sphere.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201511013835.1A CN105443816B (en) | 2015-12-31 | 2015-12-31 | Diesel engine high-pressure co-rail two-stage pressure limiting valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201511013835.1A CN105443816B (en) | 2015-12-31 | 2015-12-31 | Diesel engine high-pressure co-rail two-stage pressure limiting valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105443816A CN105443816A (en) | 2016-03-30 |
| CN105443816B true CN105443816B (en) | 2017-11-14 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201511013835.1A Active CN105443816B (en) | 2015-12-31 | 2015-12-31 | Diesel engine high-pressure co-rail two-stage pressure limiting valve |
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| CN (1) | CN105443816B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106593730B (en) * | 2016-12-08 | 2018-08-07 | 中国北方发动机研究所(天津) | A kind of high-pressure common rail variable pump testing pressure-regulating valve |
| CN108005746B (en) * | 2017-12-29 | 2024-04-16 | 潍柴动力股份有限公司 | Engine main oil duct pressure limiting valve and engine |
Citations (6)
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|---|---|---|---|---|
| DE10261415B3 (en) * | 2002-12-30 | 2004-07-08 | Siemens Ag | Press matching device for fuel injection system for automobile IC engine has passive valve module provided with leakage opening opened upon loss of fuel flow and closed upon high fuel flowrate |
| DE102006025926A1 (en) * | 2006-06-02 | 2007-12-06 | Siemens Ag | Pressure control valve for use in common rail diesel fuel injection system, has spring acting on closing body blocking fuel supply line, where body is formed as rotation symmetric body supporting spring in force-fit and form-fit manner |
| CN103502710A (en) * | 2011-04-29 | 2014-01-08 | 罗伯特·博世有限公司 | Pressure-limiting valve |
| CN104302907A (en) * | 2012-05-16 | 2015-01-21 | 福士汽车配套部件责任有限公司 | Pressure-limiting valve |
| CN104781545A (en) * | 2012-09-17 | 2015-07-15 | 罗伯特·博世有限公司 | Pressure control valve for a fuel injection system |
| CN205244515U (en) * | 2015-12-31 | 2016-05-18 | 重庆红江机械有限责任公司 | Diesel engine is two -stage voltage limiting valve for high pressure common rail |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10115162C1 (en) * | 2001-03-27 | 2002-10-02 | Orange Gmbh | Pressure relief valve for fuel injectors |
-
2015
- 2015-12-31 CN CN201511013835.1A patent/CN105443816B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10261415B3 (en) * | 2002-12-30 | 2004-07-08 | Siemens Ag | Press matching device for fuel injection system for automobile IC engine has passive valve module provided with leakage opening opened upon loss of fuel flow and closed upon high fuel flowrate |
| DE102006025926A1 (en) * | 2006-06-02 | 2007-12-06 | Siemens Ag | Pressure control valve for use in common rail diesel fuel injection system, has spring acting on closing body blocking fuel supply line, where body is formed as rotation symmetric body supporting spring in force-fit and form-fit manner |
| CN103502710A (en) * | 2011-04-29 | 2014-01-08 | 罗伯特·博世有限公司 | Pressure-limiting valve |
| CN104302907A (en) * | 2012-05-16 | 2015-01-21 | 福士汽车配套部件责任有限公司 | Pressure-limiting valve |
| CN104781545A (en) * | 2012-09-17 | 2015-07-15 | 罗伯特·博世有限公司 | Pressure control valve for a fuel injection system |
| CN205244515U (en) * | 2015-12-31 | 2016-05-18 | 重庆红江机械有限责任公司 | Diesel engine is two -stage voltage limiting valve for high pressure common rail |
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|---|---|
| CN105443816A (en) | 2016-03-30 |
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