CN201818412U - Low pressure difference hydraulic sealing high pressure co-rail fuel pump - Google Patents
Low pressure difference hydraulic sealing high pressure co-rail fuel pump Download PDFInfo
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- CN201818412U CN201818412U CN2010205862825U CN201020586282U CN201818412U CN 201818412 U CN201818412 U CN 201818412U CN 2010205862825 U CN2010205862825 U CN 2010205862825U CN 201020586282 U CN201020586282 U CN 201020586282U CN 201818412 U CN201818412 U CN 201818412U
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Abstract
The utility model relates to a low pressure difference hydraulic sealing high pressure co-rail fuel pump, mainly comprising a pump body, a plunger, an oil outlet one-way valve, an oil inlet one-way valve, a low pressure difference control valve, a synchronous pressure lifter and a lubricating oil inlet one-way valve. The low pressure difference control valve and the synchronous pressure lifter controls synchronous lifting and lowering of oil pressures at a lubricating end and a fuel oil end at the cooperating gap of the plunger and the work oil cylinder, and keep a small pressure difference by which the lubricating oil pressure is higher than the fuel oil pressure, preventing fuel oil from flowing into the cooperating gap of the plunger and the work oil cylinder. The low pressure difference hydraulic sealing high pressure co-rail fuel pump in the utility model solves problem of leakage of high pressure fuel oil, the fuel oil pressure is higher than 2200 bar, guaranteeing lubrication of precision sliding fit surface between the plunger and the work oil cylinder, and improving work reliability and endurance, a superhigh pressure fuel oil injection system can further reduce fuel oil consumption rate and emission, and can be used for diesel engine combusting low viscosity substitution fuels such as dimethyl ether, etc.
Description
Technical field:
The utility model belongs to technical field of internal combustion engines.Relate generally to the diesel engine high-pressure co-rail fueling injection equipment, be specially a kind of low differential pressure liquid packing high-pressure common rail fuel pump.
Technical background:
Diesel engine thermal efficiency height has become widely used motor.Diesel fuel injection system is the critical component that influences diesel engine fuel consumption rate and discharging, for reducing fuel consumption rate and discharging, each state is all constantly making improvements, diesel engine is since 1892 are born, and its fuel injection system presses oil level to put the controlling type electric control fuel oil jet system by mechanical fuel ejecting system, first generation cam and second generation cam presses solenoid controlling type electric control fuel oil jet system to develop into present third generation Electrocontrolled high-pressure common rail fuel injection system.Because world energy sources deficiency, price sharp rise and the Abgasgesetz of various countries severe day by day, for adapting to current and the Abgasgesetz in the future and the market demand that reduces fuel consumption rate, diesel engine needs the more high pressure fuel pump of high injection pressure, the diesel oil that sprays into the firing chamber is mixed more equably with air and fully burning, and further reduce oil consumption rate and exhaust emission.Petroleum resources reduce also needs diesel fuel injection system can spray low viscosity alternative fuel such as dimethyl ether.
Existing high pressure common rail electric-controlled injection system all is to adopt the plunger type high-pressure fuel pump, the gap that is slidingly matched of plunger and plunger bushing relies on the lubricated and sealing of fuel oil, existing high pressure fuel altogether the rail pump solve the method for leaking be with plunger bushing that plunger cooperates on add the release oil-return groove of an annular, make the fuel oil of leakage flow back to fuel tank through back oil road from oil-return groove, gap intermediate fuel oil leakage rate improves with the pump oil pressure and increases, serious fuel leakage causes setting up the above superelevation fuel pressure of 2000bar, the oil pressure of current high-pressure common rail high pressure fuel pump reaches 2000bar seldom in 1600～1800bar scope.Along with fuel pressure increases, the problem that is difficult to set up the ultrahigh pressure fuel pressure due to the high pressure fuel pump fuel oil excessive leakage is the technical barrier in the development of high-pressure common rail oil-fired system always, also is the technical barrier that low viscosity alternative fuel such as dimethyl ether fuel need solve.
The applicant's utility model patent (patent No.: ZL 2,006 1 0127615.1) " multifuel diesel Injection Pump " adopts in the gap of opening on the plunger bushing between oil groove usefulness high-tension lubrication oil seal and lubricated plunger and the plunger bushing, because the interior fuel oil oil pressure of the oil cylinder of plunger end face constantly raise and the reduction variation when descending oil suction of plunger and up pump were oily, the pressure reduction that alternation changes surpasses 1000bar, lubricant oil entered fuel oil and burn oil occurs when the extreme pressure lubricant oil pressure of constant voltage was higher than the fuel oil oil pressure of variation, the problem of stifled oil nozzle nozzle opening, when the lubricant oil oil pressure is lower than the fuel oil oil pressure of variation, low-viscosity fuels such as dimethyl ether enter plunger and plunger bushing matching gap, wearing and tearing and fuel leak problem occur.
Summary of the invention:
The purpose of this utility model is exactly the problem that will overcome above-mentioned high-pressure common rail fuel pump fuel leakage, and a kind of do not have fuel leakage, high-pressure common rail fuel pump that the pump oil pressure is higher are provided.
The utility model is to adopt following technological scheme to realize:
A kind of low differential pressure liquid packing formula high-pressure common rail fuel pump comprises the pump housing 1, plunger 2, fuel-displaced one-way valve 4, in line check valve 5, lubricant oil one-way valve 7, low differential pressure control valve 6, it is characterized in that: also comprise simultaneous pressure lift device 3; Be provided with operating cylinder 1.1 in the described pump housing 1, operating cylinder 1.1 upper ends are communicated with fuel-displaced one-way valve 4 through oil road R1, and fuel-displaced one-way valve 4 rail high-pressure oil pipe interface R2 together is connected; Described operating cylinder 1.1 upper ends are connected with pressure synchronization lifting device 3 and in line check valve 5 respectively through operating cylinder oil duct R3, in line check valve 5 is connected with low differential pressure control valve 6 and low-voltage fuel interface tube R4 respectively through fuel oil road R5, plunger 2 is contained in the operating cylinder 1.1, and be accurate being slidingly matched with operating cylinder 1.1, be provided with the oil groove R10 of annular on the fitting surface of the operating cylinder 1.1 that is slidingly matched with plunger 2, oil groove R10 is communicated with described simultaneous pressure lift device 3 and lubricant oil one-way valve 7 respectively through oil groove oil duct R9; Described lubricant oil one-way valve 7 is connected with pressure lubrication tubing interface R8 through low differential pressure oil leab R7, low differential pressure control valve 6, oil leab R6; The top of described plunger 2 is communicated with operating cylinder 1.1 with the upper end of the matching gap J1 of operating cylinder 1.1, the lower end is communicated with oil groove R10.
Described simultaneous pressure lift device 3 comprises simultaneous pressure oil cylinder 3.5, pressure balance piston 3.2, pressure balance spring 3.4; Described pressure balance piston 3.2 is contained in the simultaneous pressure oil cylinder 3.5 and is accurate being slidingly matched with the simultaneous pressure oil cylinder, the lower end of the upper-end surface of pressure balance piston 3.2 and pressure balance spring 3.4 joins, and the upper-end surface of the upper end of pressure balance spring 3.4 and simultaneous pressure oil cylinder 3.5 joins; Described pressure balance piston 3.2 is divided into top simultaneous pressure fuel oil cylinder 3.3 and the lubricated oil cylinder 3.1 of bottom simultaneous pressure with simultaneous pressure oil cylinder 3.5, top simultaneous pressure fuel oil cylinder 3.3 is connected with operating cylinder 1.1 and in line check valve 5 respectively through work oil duct oil cylinder R3, the lubricated oil cylinder 3.1 of bottom simultaneous pressure through oil groove oil duct R9 respectively with oil groove R10 and advance lubricant oil one-way valve 7 and be connected.
The beneficial effects of the utility model:
1, the high pressure fuel pump that the utility model has solved in the existing high-pressure common rail fueling injection equipment with imitating improves the quantity of fuel leakage increase with the pump oil pressure, the problem that fuel leakage restriction pump oil pressure improves, realized that high pressure fuel pump does not have fuel leakage superpressure pump oil, and guaranteed precision between plunger and the operating cylinder the lubricated of face that be slidingly matched, functional reliability and working life have been improved, pump oil oil pressure can reach more than the 2200bar, the pump oil pressure that is higher than existing high-pressure common rail fuel pump, higher fuel pressure can make the diesel oil that sprays into the firing chamber mix more equably with air, burning further reduces fuel consumption rate and exhaust emission more fully.
2, the utility model has stoped the matching gap that fuel oil enters plunger and operating cylinder effectively, has guaranteed lubricated and sealing, can spray low viscosity alternative fuel such as dimethyl ether.
Description of drawings:
Fig. 1 is the structural representation of a low differential pressure liquid packing high-pressure common rail fuel pump of the present utility model.
Among Fig. 1: 1, the pump housing; 1.1 operating cylinder; 2, plunger; 3, simultaneous pressure lift device; 3.1, the lubricated oil cylinder of simultaneous pressure; 3.2, the pressure balance piston; 3.3, simultaneous pressure fuel oil cylinder; 3.4, pressure balance spring; 3.5, the simultaneous pressure oil cylinder; 4, fuel-displaced one-way valve; 5, in line check valve; 6, low differential pressure control valve; 6.1, the fuel oil cylinder; 6.2, the low differential pressure spring; 6.3 pressure difference valve; 6.4, the low differential pressure valve opening; 6.5, annular oil-feed tank; 6.6, lubricated oil cylinder; 6.7, oil cylinder; 7, advance the lubricant oil one-way valve; 8, plunger actuation mechanism; 8.1, driving cam; 8.2, roller, 8.3, roller shaft; 8.4, tappet; 8.5, spring seat; 8.6, plunger return spring; 8.7, camshaft case; R1, oil road; R2, common rail high-pressure oil pipe interface; R3, operating cylinder oil duct; R4, low-voltage fuel interface tube; R5, fuel oil road; R6, oil leab; R7, low differential pressure oil leab; R8, pressure lubrication tubing interface; R9, oil groove oil duct; R10, oil groove; R11, return tube interface; The upper end of the matching gap of J1, plunger 2 and operating cylinder 1.1; The lower end of the matching gap of J2, plunger 2 and operating cylinder; The matching gap of J3, tappet and the pump housing; K1 tappet chamber; K2, camshaft case.
Embodiment:
Below in conjunction with accompanying drawing embodiment of the present utility model is further described.
As shown in Figure 1, the utility model low differential pressure liquid packing high-pressure common rail fuel pump.It mainly comprises the pump housing 1, plunger 2, plunger actuation mechanism 8, fuel-displaced one-way valve 4, in line check valve 5, low differential pressure control valve 6, simultaneous pressure lift device 3 and lubricant oil one-way valve 7.
Be provided with operating cylinder 1.1 in the described pump housing 1, operating cylinder 1.1 upper ends are communicated with fuel-displaced one-way valve 4 through oil road R1, fuel-displaced one-way valve 4 rail high-pressure oil pipe interface R2 together is connected, operating cylinder 1.1 upper ends also are connected with pressure synchronization lifting device 3 and in line check valve 5 respectively through operating cylinder oil duct R3, in line check valve 5 is connected with low differential pressure control valve 6 and low-voltage fuel interface tube R4 respectively through fuel oil road R5, plunger 2 is contained in the operating cylinder 1.1, be accurate being slidingly matched with operating cylinder 1.1, matching gap is 0.002～0.004 millimeter scope, on the fitting surface of the operating cylinder 1.1 that is slidingly matched with plunger 2, be provided with the oil groove R10 of annular, oil groove R10 respectively with simultaneous pressure lift device 3 and advance lubricant oil one-way valve 7 and be communicated with, advances lubricant oil one-way valve 7 through low differential pressure oil leab R7 through oil groove oil duct R9, low differential pressure control valve 6, oil leab R6 is connected with pressure lubrication tubing interface R8; Plunger 2 be communicated with operating cylinder 1.1 with the upper end of matching gap J1 operating cylinder 1.1, the lower end of matching gap J1 is communicated with oil groove R10; The bottom of plunger 2 is communicated with oil groove R10 with the upper end of the matching gap J2 of operating cylinder 1.1, the lower end is connected with return tube interface R11 with matching gap J3, the camshaft chest K2 of the pump housing 1 through the K1 of spring housing, tappet 8.4.
Described low differential pressure control valve 6 comprises oil cylinder 6.7, annular oil-feed tank 6.5, pressure difference valve 6.3, low differential pressure spring 6.2, pressure difference valve 6.3 is contained in the oil cylinder 6.7, be accurate being slidingly matched with oil cylinder 6.7, matching gap is 0.002～0.004 millimeter scope, on the fitting surface of the oil cylinder 6.7 that cooperates with pressure difference valve 6.3, be provided with the oil-feed tank 6.5 of annular, annular oil-feed tank 6.5 is connected with pressure lubrication tubing interface R8 through oil leab R6, the upper-end surface of pressure difference valve 6.3 is connected with the lower end of low differential pressure spring 6.2, the upper end of low differential pressure spring 6.2 is connected with the end face of oil cylinder 6.7, pressure difference valve 6.3 is divided into the fuel oil cylinder 6.1 of upper end and the lubricated oil cylinder 6.6 of lower end with oil cylinder 6.7, low differential pressure valve opening 6.4 in the pressure difference valve 6.3 is connected with lubricated oil cylinder 6.6, low differential pressure valve opening 6.4 also is connected with annular oil groove 6.5, and the fuel oil cylinder 6.1 on low pressure difference limen 6 tops is connected with fuel oil road R5, the lubricated oil cylinder 6.6 of bottom through low differential pressure oil leab R7 with advance lubricant oil one-way valve 7 and be connected.
Described simultaneous pressure lift device 3 comprises simultaneous pressure oil cylinder 3.5, pressure balance piston 3.2, pressure balance spring 3.4, pressure balance piston 3.2 is contained in the simultaneous pressure oil cylinder 3.5 and is accurate being slidingly matched with the simultaneous pressure oil cylinder, matching gap is 0.002～0.004 millimeter scope, the upper-end surface of pressure balance piston 3.2 is connected with the lower end of pressure balance spring 3.4, the upper end of pressure balance spring 3.4 is connected with the upper-end surface of simultaneous pressure oil cylinder 3.5, pressure balance piston 3.2 is divided into simultaneous pressure oil cylinder 3.5 in the simultaneous pressure fuel oil cylinder 3.3 and the lubricated oil cylinder 3.1 of the simultaneous pressure of bottom on top, simultaneous pressure fuel oil cylinder 3.3 is connected with operating cylinder through work oil duct oil cylinder R3, and the lubricated oil cylinder 3.1 of simultaneous pressure is connected with oil groove R10 through oil leab oil groove R9;
Used low differential pressure liquid packing working principle is in the utility model:
Be communicated with operating cylinder (1.1) with the upper end of matching gaps operating cylinder (1.1) (J1) plunger (2), the lower end of matching gap J1 is through oil groove R10, oil groove oil duct R9 is connected with the lubricated oil cylinder 3.1 of simultaneous pressure, the lubricant oil oil pressure of matching gap J1 lower end equates with the lubricant oil oil pressure Pj3 that simultaneous pressure is lubricated in the oil cylinder 3.1, the upper end of matching gap J1 is through operating cylinder 1.1, operating cylinder oil duct R3 communicates with simultaneous pressure fuel oil cylinder 3.3, and the fuel oil oil pressure of matching gap J1 upper end equates with the fuel oil oil pressure Pr2 in the simultaneous pressure fuel oil cylinder 3.3; The lubrication pressure Pj that enters pressure lubrication tubing interface R8 is greater than the fuel pressure Pr that enters low-voltage fuel interface tube R4, i.e. Pj＞Pr+4bar; 6 controls of low pressure difference limen enter into by low pressure difference limen 6 through low differential pressure oil leab R7 through oil leab R6 from pressure lubrication tubing interface R8, and the lubrication pressure Pj2 of lubricant oil one-way valve 7 is higher than the small pressure reduction of fuel oil pressure Pr that enters oiling valve 5 from low-voltage fuel interface tube R4 through fuel oil road R5, be Pj2＞Pr, Pj2=Pr+1bar; Close during the oil pressure Pr2 of in line check valve 5 in plunger 2 up oil cylinders 1.1 〉=Pr, advance lubricant oil one-way valve 7 and in oil groove oil duct R9, close during lubrication pressure Pj3 〉=Pj2; Simultaneous pressure lift device 3 upper ends through operating cylinder oil duct R3 be communicated with operating cylinder 1.1, the lower end is communicated with oil groove R10 through oil groove oil duct R9, in the working procedure of plunger process pump oil and oil-feed about in the of 2, simultaneous pressure lift device 3 keeps the fuel oil oil pressure Pr2 synchronization lifting of (upper end of gap J1) among the lubrication pressure Pj3 and operating cylinder 1.1 of (lower end of gap J1) among the oil groove R10 and keeps a low pressure reduction, be Pj3＞Pr2, Pj3=Pr2+1bar, stop the fuel oil of the low relatively 1bar of oil pressure to enter gap J1, thereby do not had fuel leakage.
The working procedure of the utility model low differential pressure liquid packing high-pressure common rail fuel pump is:
The lubricant oil oil pressure Pj that enters annular oil-feed tank 6.5 through pressure lubrication tubing interface R8, oil leab R6 is greater than the fuel oil oil pressure Pr that enters the fuel oil cylinder 6.1 of low differential pressure control valve 6 from low-voltage fuel interface tube R4 through fuel oil road R5, i.e. Pj＞Pr, Pj＞Pr-4bar;
Lubricant oil enters lubricated oil cylinder 6.6 from annular oil-feed tank 6.5 through low differential pressure valve opening 6.4, act on low pressure difference limen 6.3 lower end lubricant oil oil pressure greater than upper end low-voltage fuel oil pressure, low pressure difference limen 6.3 up compression and low pressure difference springs 6.2 to low differential pressure valve opening 6.4 and being connected of annular oil-feed tank 6.5 disconnects and stops into lubricant oil, and low pressure difference limen 6.3 stops up; It is 1bar at the oil pressure that lubricated oil cylinder 6.6 produces that selected low differential pressure spring 6.2 elastic force at this moment acts on low pressure difference limen 6.3, low differential pressure spring promotion low pressure difference limen 6.3 is descending when the oil pressure in the lubricated oil cylinder 6.6 descends, low differential pressure valve opening 6.4 is communicated with annular oil-feed tank 6.5 again, lubricant oil enters lubricated oil cylinder 6.6 from annular oil-feed tank 6.5 through low differential pressure valve opening 6.4 again, lubrication pressure in the lubricated oil cylinder 6.6 rises to low pressure difference limen 6.3 up low differential pressure valve openings 6.4 again and stops oil-feed with oil-feed tank 6.5 disconnections, oil pressure reaches till the lubrication pressure Pj2, i.e. Pj2=Pr+1bar; The middle lubricant oil oil pressure Pj2 of low differential pressure control valve control this moment low differential pressure oil leab R7 is than the high 1bar of fuel oil oil pressure Pr among the fuel oil road R5; Fuel oil oil pressure in the operating cylinder 1.1 is Pr2, and the lubricant oil oil pressure is Pj3 in the oil groove, and plunger actuation mechanism 8 drive plunger 2 pump, and when 1.1 oil-feeds of plunger 2 downlink working oil cylinders, in line check valve 5 is open-minded, at this moment Pr2≤Pr; The short flow resistance of oil duct is little, Pr2=Pr when disregarding flowing pressure loss.Wherein:
Lubrication pressure Pj, lubrication pressure is Pj2, the lubricant oil oil pressure is Pj3 in the oil groove;
The fuel oil oil pressure of fuel oil cylinder is Pr, and the fuel oil oil pressure in the operating cylinder is Pr2.
Lubricant oil oil pressure Pr2 among the low differential pressure oil leab R7 is delivered to lubricated oil cylinder 3.1 of simultaneous pressure and oil groove R10 through advancing lubricant oil one-way valve 7 with oil groove oil duct R9 simultaneously, this moment, matching gap J1 lower end machine oil hydraulic Pj3 equaled lubrication pressure Pj2, i.e. Pj3=Pj2=Pr+1bar; Simultaneously the lubricant oil oil pressure of plunger 2 and the lower end of the matching gap J1 of operating cylinder 1.1 is greater than the fuel oil oil pressure of upper end, i.e. Pj3=Pr+1bar=Pr2+1bar, and Pj3＞Pr2 has stoped fuel oil to enter matching gap J1, no fuel leakage; Test confirms at plunger 2 and operating cylinder 1.1 matching gap J1 in the minimum length of 0.002～0.004 millimeter scope, matching gap J1 greater than under 5 millimeters, the condition of oil pressure difference less than 5bar at J1 two ends, gap, lubricant oil among the J1 of gap does not have flow phenomenon, and promptly lubricant oil can not flow into operating cylinder 1.1 yet; Pressure balance piston 3.2 lower end surface oil pressure (Pj3) are greater than upper-end surface oil pressure (Pr2) in this moment simultaneous pressure lift device 3, when the pressure balance piston is increased to by the up compression pressure balance spring 3.4 of 1bar differential pressure action to pressure balance spring 3.4 elastic force to act on the pressure balance of lower end surface of equalizing piston 3.2 with the 1bar oil pressure, be the elastic force of pressure balance spring 3.4 when acting on oil pressure that pressure balance piston 3.2 produces being 1bar in the lubricated oil cylinder 3.1 of simultaneous pressure, pressure balance piston 3.2 stops up; When plunger 2 up pumps are oily, operating cylinder 1.1 oil pressure raise, oil pressure transmits to fuel oil road R5 in the in line check valve blocking-up operating cylinder 1.1, oil pressure is along with oil pressure Pr2 in the operating cylinder 1.1 raises synchronously in the simultaneous pressure fuel oil cylinder 3.3, pressure balance piston 3.2 is delivered to lubricated oil cylinder 3.1 of simultaneous pressure and oil groove R10 with the elastic force of fuel pressure in the simultaneous pressure fuel oil cylinder 3.3 and pressure balance spring 3.4, the oil pressure that advances the 7 blocking-up risings of lubricant oil one-way valve transmits to oil leab R8, lubricant oil oil pressure Pj3 among the oil groove R10 is higher than fuel oil oil pressure Pr2 at this moment, little pressure reduction, i.e. a Pj3=Pr2+1bar are arranged; The lubricant oil oil pressure Pj3 of the matching gap J1 lower end of plunger 2 and operating cylinder 1.1 presses oil pressure Pr2 greater than the fuel oil in the operating cylinder 1.1 of matching gap J1 upper end, be Pj3=Pr2+1bar, Pj3＞Pr2 has stoped fuel oil to enter matching gap J1, and plunger 2 up pumps do not have fuel leakage yet when oily; The lubricant oil that remains among the J1 of gap plays sealing with lubricated, lubricant oil lubricate among the J2 of gap, because lubricating oil viscosity is big, J2 gap minimum (less than 4 μ m), the lubricant oil that from the J2 of gap, releases seldom, the lubricant oil that releases flows back to lubricating oil tank through matching gap J3, the camshaft case K2 of tappet chamber K1, tappet 8.4 and the pump housing 1 from return tube interface R11.When the oil pressure in the operating cylinder 1.1 was higher than oil pressure in the injection line, high pressure fuel pumped into injection line through oil road R1, high pressure fuel interface tube R2; Fuel-displaced one-way valve 4 was closed when plunger 2 went upward to top dead center, stopped pump oil, the descending oil-feed process that repeats again of plunger 2 beginnings.
Low differential pressure liquid packing formula high-pressure common rail fuel pump of the present utility model is in the process of oil-feed and high-pressure service pump oil, the lubricant oil oil pressure of the lubricant oil end of plunger 2 and operating cylinder 1.1 matching gap J1 is with fuel oil end fuel oil oil pressure synchronization lifting, and keep lubricant oil oil pressure Pj3 to be higher than fuel oil oil pressure Pr2, little pressure reduction, i.e. a Pj3=Pr2+1bar are arranged; The lubricant oil oil pressure has stoped the high pressure fuel of the low relatively 1bar of oil pressure to leak, make pump oil oil pressure can be higher than 2200bar, be higher than the existing oil of rail high-pressure injection pump pump altogether oil pressure, and guaranteed plunger 2 and operating cylinder 1.1 precisions the lubricated of face that be slidingly matched, improved functional reliability and durability.And can be used for low-viscosity fuels such as diesel engine dimethyl ether fuel.
Claims (2)
1. low differential pressure liquid packing formula high-pressure common rail fuel pump, comprise the pump housing (1), plunger (2), fuel-displaced one-way valve (4), in line check valve (5), lubricant oil one-way valve (7), low differential pressure control valve (6), it is characterized in that: also comprise simultaneous pressure lift device (3); Be provided with operating cylinder (1.1) in the described pump housing (1), operating cylinder (1.1) upper end is communicated with fuel-displaced one-way valve (4) through oil road R1, and fuel-displaced one-way valve (4) rail high-pressure oil pipe interface (R2) together is connected; Described operating cylinder (1.1) upper end is connected with pressure synchronization lifting device (3) and in line check valve (5) respectively through operating cylinder oil duct (R3), in line check valve (5) is connected with low differential pressure control valve (6) and low-voltage fuel interface tube (R4) respectively through fuel oil road (R5), plunger (2) is contained in the operating cylinder (1.1), and be accurate being slidingly matched with operating cylinder (1.1), be provided with the oil groove (R10) of annular on the fitting surface of the operating cylinder (1.1) that is slidingly matched with plunger (2), oil groove (R10) is communicated with described simultaneous pressure lift device (3) and lubricant oil one-way valve (7) respectively through oil groove oil duct (R9); Described lubricant oil one-way valve (7) is connected with pressure lubrication tubing interface (R8) through low differential pressure oil leab (R7), low differential pressure control valve (6), oil leab (R6); Described plunger (2) be communicated with operating cylinder (1.1) with the upper end of matching gaps operating cylinder (1.1) (J1), the lower end of matching gap (J1) is communicated with oil groove (R10).
2. low differential pressure liquid packing formula high-pressure common rail fuel pump according to claim 1, it is characterized in that: described simultaneous pressure lift device (3) comprises simultaneous pressure oil cylinder (3.5), pressure balance piston (3.2), pressure balance spring (3.4); Described pressure balance piston (3.2) is contained in the simultaneous pressure oil cylinder (3.5) and is accurate being slidingly matched with the simultaneous pressure oil cylinder, the lower end of the upper-end surface of pressure balance piston (3.2) and pressure balance spring (3.4) joins, and the upper-end surface of the upper end of pressure balance spring (3.4) and simultaneous pressure oil cylinder (3.5) joins; Described pressure balance piston (3.2) is divided into top simultaneous pressure fuel oil cylinder (3.3) and the lubricated oil cylinder (3.1) of bottom simultaneous pressure with simultaneous pressure oil cylinder (3.5), top simultaneous pressure fuel oil cylinder (3.3) is connected with operating cylinder (1.1) and in line check valve (5) respectively through work oil duct oil cylinder (R3), the bottom simultaneous pressure lubricate oil cylinder (3.1) through oil groove oil duct (R9) respectively with oil groove (R10) and advance lubricant oil one-way valve (7) and be connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205862825U CN201818412U (en) | 2010-10-29 | 2010-10-29 | Low pressure difference hydraulic sealing high pressure co-rail fuel pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205862825U CN201818412U (en) | 2010-10-29 | 2010-10-29 | Low pressure difference hydraulic sealing high pressure co-rail fuel pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201818412U true CN201818412U (en) | 2011-05-04 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010205862825U Expired - Lifetime CN201818412U (en) | 2010-10-29 | 2010-10-29 | Low pressure difference hydraulic sealing high pressure co-rail fuel pump |
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| CN (1) | CN201818412U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8960159B2 (en) | 2012-07-31 | 2015-02-24 | Caterpillar Inc. | Drain for fuel pump |
| CN107956618A (en) * | 2016-10-18 | 2018-04-24 | 上海夏雪科技有限公司 | Internal combustion engine |
| CN113931728A (en) * | 2021-01-19 | 2022-01-14 | 吉利汽车研究院（宁波）有限公司 | Oil vapor control method, device and system and storage medium |
-
2010
- 2010-10-29 CN CN2010205862825U patent/CN201818412U/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8960159B2 (en) | 2012-07-31 | 2015-02-24 | Caterpillar Inc. | Drain for fuel pump |
| CN107956618A (en) * | 2016-10-18 | 2018-04-24 | 上海夏雪科技有限公司 | Internal combustion engine |
| CN113931728A (en) * | 2021-01-19 | 2022-01-14 | 吉利汽车研究院（宁波）有限公司 | Oil vapor control method, device and system and storage medium |
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