CN106014737A - Combined type damping structure capable of meeting low NVH noise of high-pressure oil pump of GDI engine - Google Patents
Combined type damping structure capable of meeting low NVH noise of high-pressure oil pump of GDI engine Download PDFInfo
- Publication number
- CN106014737A CN106014737A CN201610417025.0A CN201610417025A CN106014737A CN 106014737 A CN106014737 A CN 106014737A CN 201610417025 A CN201610417025 A CN 201610417025A CN 106014737 A CN106014737 A CN 106014737A
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- valve
- valve rod
- spool
- oil pump
- damping structure
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- 238000013016 damping Methods 0.000 title claims abstract description 76
- 230000033001 locomotion Effects 0.000 claims abstract description 16
- 206010008469 Chest discomfort Diseases 0.000 claims description 7
- 230000009471 action Effects 0.000 claims description 3
- 230000001360 synchronised effect Effects 0.000 claims description 2
- 238000003466 welding Methods 0.000 claims description 2
- 230000000694 effects Effects 0.000 abstract description 9
- 230000009467 reduction Effects 0.000 abstract description 6
- 239000003921 oil Substances 0.000 description 31
- 239000000295 fuel oil Substances 0.000 description 10
- 238000002347 injection Methods 0.000 description 9
- 239000007924 injection Substances 0.000 description 9
- 239000000446 fuel Substances 0.000 description 8
- 239000000203 mixture Substances 0.000 description 7
- 238000005516 engineering process Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 3
- 230000004044 response Effects 0.000 description 3
- 230000033228 biological regulation Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- 238000000889 atomisation Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 230000008447 perception Effects 0.000 description 1
- 230000000979 retarding effect Effects 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
Classifications
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Magnetically Actuated Valves (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention discloses a combined type damping structure capable of meeting the low NVH noise of a high-pressure oil pump of a GDI engine. The combined type damping structure comprises a valve element, a damping piece, a valve rod and a valve supporting seat; overflowing holes are distributed in the valve element, the valve element is fixed to one end of the valve rod, and the other end of the valve rod is matched with a center hole of the valve supporting seat; the damping piece is fixed to the valve element, throttling holes are distributed in the damping piece and right face the overflowing holes in the valve element, and the diameter of the throttling holes is smaller than that of the overflowing holes; the valve element, the damping piece and the valve rod synchronously move, through the throttling effect of the throttling holes, the motion speed of the valve rod is reduced, and the valve supporting seat limits movement of the valve rod in the direction of the axis line of the center hole of the valve supporting seat; and the small hole throttling principle is ingeniously utilized for achieving the speed reduction brake function of a motion assembly composed of the valve element inside the high-pressure oil pump and the valve rod, starting from the source of noise generation, the high frequency and the harsh impact noise generated by the high-pressure oil pump are reduced, and the design standard of the NVH noise of the engine is well met.
Description
Technical field
The invention belongs to high-pressure oil pump of engine field, be specifically related to the combination type damping structure of high-pressure oil pump electromagnetic valve.
Background technology
For adapting to the laws and regulations requirements such as the strictest national oil consumption, discharge, in the urgent need to developing low oil consumption, the electromotor of satisfied more maximum discharge standard, GDI(gasoline direct injection in a kind of cylinder improving the fuel-injection pressure of electromotor, inner cylinder direct injection) technology is commonly used by international and domestic manufacturer, while the fuel oil reducing electromotor consumes, also can meet the requirement of more maximum discharge regulation.The application of GDI technology in cylinder, while creating higher value to people, also brings more hang-up to manufacturer.
After using in-cylinder direct-jet technology, the fuel-injection pressure of electromotor is obviously improved, improves fuel atomization effect, reduce complete machine discharge, reduction fuel oil consumption, but the problem the most simultaneously occurring in that the noise of high-pressure oil pump.The high-pressure fuel injection pump assembly structure of electromotor as shown in Figure 6, is made up of parts such as electromagnetic valve, mounting flange 6, oil suction chamber 9, delivery valve structure 8, high pressure chest structure 7 and piston structures.High-pressure fuel injection pump assembly operation principle is to drive the plunger of high pressure chest structure to move upward by rotating of camshaft, fuel oil quality in compression high pressure chest, the highest can by fuel pressure improve to 49 times, fuel oil after compression, depended on pressure is poor, promotes delivery valve structure, and high pressure fuel flows out, otherwise, then delivery valve cuts out.The oil-feed of high-pressure oil pump is by battery valve control, battery valve is provided with valve module 10, common valve module is supported seat 4 by spool 1, valve rod 3 and valve and forms, such as Fig. 7 indication, its operation principle is: course of normal operation, under the effect of electromagnetic force, spool 1 supports the motion of seat 4 direction with the moving parts of valve rod 3 composition to deviating from valve, keeps quickly response.In the case of disconnecting electromagnetic force, spool 1 supports the motion of seat 4 direction to valve under spring force with the moving parts of valve rod 3 composition, fuel oil flows through the flowing hole 1-2 on spool 1, but owing to the overflow section in this hole is bigger, almost without throttling action, valve rod 3 props up bearing 4 with bigger kinetic energy impact valve, thus produces high frequency and harsh noise.This noise can be had a strong impact on the overall comfort of car steering by obvious perception under car load idling operation.
Therefore, the noise of this type high-pressure oil pump how is reduced, it has also become problem demanding prompt solution.
Summary of the invention
The present invention is directed to the deficiency that prior art exists, it is provided that the combination type damping structure of a kind of electromagnetic valve, reduce the noise of GDI engine high-pressure oil pump.
Technical scheme is as follows:
A kind of combination type damping structure meeting GDI engine high-pressure oil pump low NVH noise, supports seat including spool, damping fin, valve rod and valve.Flowing hole is distributed on described spool, and spool is fixed on valve rod one end, and the centre bore that the valve rod other end supports seat with valve coordinates.Being fixed with damping fin on described spool, throttle orifice is distributed on damping fin, throttle orifice is the most right with the flowing hole on spool, and aperture is less than the aperture of flowing hole；Spool, damping fin are synchronized with the movement with valve rod, by the throttling action of throttle orifice, reduce the movement velocity of valve rod, and valve supports seat and limits moving along its centre bore direction of axis line of valve rod.
The present invention is applied to inside the electromagnetic valve of high-pressure fuel injection pump assembly, it it is the improvement to valve module, its operation principle is as follows: course of normal operation, and combination type damping structure is in one and is full of and the fuel oil closing intracavity of low pressure oil way uniform pressure (general low pressure oil way pressure is between 3.5Bar～6.8Bar).Under the effect of electromagnetic force, the moving parts of spool, damping fin, valve rod composition supports the motion of seat direction to deviating from valve, keeps quickly response.In the case of disconnecting electromagnetic force, spool, damping fin, the moving parts of valve rod composition is supported seat direction by the effect of spring force to valve and moves, owing to fuel oil flows through throttle orifice on damping fin, and the overflow section of this throttle orifice is the least, pressure reduction can be produced before and after throttle orifice, damping fin flowing hole with spool under the effect of pressure reduction fits tightly, fuel oil only throttle orifice outflow from damping fin, make spool, damping fin, the moving parts of valve rod composition is by a counteracting force contrary with the direction of motion, thus decrease moving parts impact valve and support the kinetic energy of seat, thus reduce the NVH noise of high-pressure oil pump.
Further, described damping fin covers on spool, both are fixed by edge high intensity, so damping fin and spool does not connect in middle major part, damping fin can be under fluid pressure to two lateral movements, it is close to play damping with spool, or does not affect the stream excessively of flowing hole away from spool.
Further, on described damping fin except arrange and supporting section discharge orifice in addition to region be engraved structure.So, at damping fin under fluid pressure after moving away from valve block direction, can be that fluid reserves enough spaces through valve block.
Further, in order to the damping of damping fin is better achieved, the region of described setting and supporting section discharge orifice is foliaceous, and blade is respectively provided with throttle orifice, and blade is connected with damping fin outer ring, is uniformly distributed in damping fin outer ring.
The present invention further provides a kind of high-pressure oil pump of engine, arrange electromagnetic valve in the oil suction chamber of described high-pressure oil pump, electromagnetic valve uses combinations of the above formula damping structure, and the spool of combination type damping structure is controlled by solenoid, and is driven reset by back-moving spring；The axle journal of the valve rod of combination type damping structure supports the centre bore of seat through valve, and end is fixed valve block, moved by valve rod band moving valve plate, closes and opens valve and support the oil inlet passage on seat, it is achieved with the break-make of high pressure chest.
It is an advantage of the current invention that the retarding braking function utilizing orifice restriction principle to realize high-pressure oil pump inner spool and the moving parts of valve rod composition dexterously, reduce, from the source producing noise, high frequency and the ear-piercing impact noise that high-pressure oil pump produces, and preferably meet the design standard of electromotor NVH noise.It addition, the design of combination type damping structure can also alleviate high-pressure oil pump weight, the design cost reducing high-pressure fuel injection pump assembly puts into, and meets the trend of the light-weight design of electromotor.
Accompanying drawing explanation
Fig. 1 is a kind of structural representation of combination type damping structure of the present invention.
Fig. 2 is a kind of structural representation of spool of the present invention.
Fig. 3 is a kind of structural representation of damping fin of the present invention.
Fig. 4 is a kind of structural representation of valve rod of the present invention.
Fig. 5 is a kind of structural representation that valve of the present invention supports seat.
Fig. 6 is the cross-sectional view of high-pressure fuel injection pump assembly.
Fig. 7 is the operation principle schematic diagram that the present invention implements front high-pressure oil pump undamped sheet.
Fig. 8 is the operation principle schematic diagram of high-pressure oil pump combination type damping structure after the present invention implements.
1-spool；2-damping fin；3-valve rod；4-valve supports seat；5-valve block；6-mounting flange；7-high pressure chest structure；8-delivery valve structure；9-oil suction chamber；10-valve module.
Detailed description of the invention
Below in conjunction with the accompanying drawings the detailed description of the invention of the present invention is described further:
Such as Fig. 1, claimed combination type damping structure includes that spool 1, damping fin 2, valve rod 3 and valve support seat 4.
As shown in Figure 2, spool 1 is cylindrical structure, external diameter Φ 20mm, and there is 1 external diameter Φ 12mm centre bore 1-1 at its center, the diameter dimension being evenly distributed with the flowing hole 1-2 of 8 external diameter Φ 3mm, centre bore 1-1 and flowing hole 1-2 around centre bore axial line 1-3 designs according to the proportionate relationship of 4:1.
As shown in Figure 3, damping fin 2 is cylindrical structure, external diameter Φ 20mm, it is distributed 8 blade 2-1 around central shaft equally distributed band throttle orifice in outer ring, throttle orifice 2-2 external diameter Φ 1mm, throttle orifice 2-2 on damping fin 2 and the flowing hole 1-2 concentric on spool 1, and on damping fin 2, throttle orifice 2-2 diameter is much smaller than the flowing hole 1-2 diameter of spool 1.
As shown in Figure 4, valve rod 3 is irregular cylinder structure, one end fixed spool 1 and damping fin 2, and the centre bore that the other end supports seat 4 with valve coordinates.The axle center 3-3 of valve rod 3 is coaxial with center spool hole axle center 1-3, and its fitting plane 3-1,3-2 match with valve block top and bottom 1-4,1-5.As it is shown in figure 5, it is a cylindrical structure that valve supports seat 4, its center is the centre bore 4-3 coordinated with valve rod 3, and circumferential distribution has oil inlet passage 4-4.The axle journal 3-5 of valve rod 3 other end supports the centre bore 4-3 matched in clearance of seat 4 with valve, between the two by the step surface 3-4 location of valve rod axle journal, and valve rod axle center 3-3 is coaxial with support seat centre bore axle center 4-2, the step surface 3-4 of valve rod axle journal contacts with valve support seat lower surface 4-1, is also the position easily producing collision noise.
The assembling structure of combination of the above formula damper structure is shown in Fig. 1, and spool 1, damping fin 2, valve rod 3, valve support seat 4 concentric.Spool 1 and damping fin 2 are integrated by the outer ring 2-3 high-intensity welding of damping fin, are assemblied on valve rod 3 by Technology for Heating Processing, are interference fit between the two, relative motion does not occur.Valve supports the axle journal 3-5 matched in clearance of centre bore 4-3 and the valve rod 3 of seat 4, the axle journal 3-5 of valve rod 3 in the centre bore 4-3 of valve-supporting seat 4 along valve rod axial line 3-3 direction side-to-side movement.The throttle orifice 2-2 of damping fin coordinates with the flowing hole 1-2 of spool 1, limits moving along its centre bore direction of axis line of valve rod 3.
See Fig. 8, combination of the above formula damper structure is applied in the high-pressure oil pump of GDI engine, the oil suction chamber of high-pressure oil pump arranges electromagnetic valve, the valve module 10 of electromagnetic valve uses combination of the above formula damping structure, the spool 1 of combination type damping structure is to be controlled by solenoid, and is driven reset by back-moving spring；The axle journal 3-5 of the valve rod of combination type damping structure supports the centre bore of seat 4 through valve, and valve block 5 is fixed in end.When electromagnetic valve work, spool 1 is by adhesive by solenoid controlled, i.e. to deviating from valve support seat 4 direction motion, keeps quickly response, and valve block 5 closes the oil inlet passage 4-4 on valve closing support seat 4.In the case of disconnecting electromagnetic force, the moving parts of spool 1, damping fin 2, valve rod 3 composition is supported seat 4 direction by the effect of spring force to valve and moves, moved by valve rod 3 band moving valve plate 5, open valve and support the oil inlet passage 4-4 on seat 4, it is achieved with the connection of high pressure chest.Throttle orifice is had on damping fin 2 owing to fuel oil flows through, and the overflow section of this throttle orifice is the least, pressure reduction can be produced before and after throttle orifice, damping fin 2 flowing hole with spool 1 under the effect of pressure reduction fits tightly, fuel oil only throttle orifice outflow from damping fin, make the moving parts that spool, damping fin, valve rod form by a counteracting force contrary with the direction of motion, thus decrease moving parts impact valve and support the kinetic energy of seat, thus reduce the NVH noise of high-pressure oil pump.
Certainly, as the case may be, above valve block, damping fin, the size of valve rod, the aperture of centre bore and flowing hole can also be other size, and the distribution of flowing hole can be 3,4,5, other quantity such as 6, and these selections all have same effect.
Claims (7)
1. meet a combination type damping structure for GDI engine high-pressure oil pump low NVH noise, support seat (4) including spool (1), damping fin (2), valve rod (3) and valve；Flowing hole (1-2) is distributed on described spool (1), and spool (1) is fixed on valve rod (3) one end, and the centre bore (4-3) that valve rod (3) other end supports seat (4) with valve coordinates, and valve supports and is provided with oil inlet passage (4-4) on seat (4)；It is characterized in that: be fixed with damping fin (2) on described spool (1), throttle orifice (2-2) is distributed on damping fin (2), and throttle orifice (2-2) is the most right with the flowing hole (2-2) on spool (1), and aperture is less than the aperture of flowing hole；Spool (1), damping fin (2) are synchronized with the movement with valve rod (3), by the throttling action of throttle orifice (2-2), reduce the movement velocity of valve rod (3), and valve supports seat (4) and limits moving along its centre bore direction of axis line of valve rod.
2. combination type damping structure as claimed in claim 1, it is characterised in that described damping fin (2) covers on spool (1), and both are fixed by edge high-intensity welding.
3. combination type damping structure as claimed in claim 1, it is characterised in that the flowing hole (1-2) of described spool (1) is around the centre bore axial line (1-3) of spool (1) and is uniformly distributed at least 3.
4. combination type damping structure as claimed in claim 1, it is characterised in that the upper region in addition to setting and supporting section discharge orifice of described damping fin (2) is engraved structure.
5. combination type damping structure as claimed in claim 3, it is characterized in that, arrange and the region of supporting section discharge orifice is foliaceous, blade (2-1) is respectively provided with throttle orifice (2-2), blade is connected with damping fin (2) outer ring, is uniformly distributed in damping fin (2) outer ring.
6. the combination type damping structure as described in any one of claim 1-4, it is characterized in that, one end that described valve rod (3) coordinates with valve support seat (4) centre bore is journal structure, axle journal (3-5) supports centre bore (4-3) matched in clearance of (4) with valve, between the two by step surface (3-4) location of valve rod axle journal, and valve rod axle center (3-3) is coaxial with support seat centre bore axle center (4-2).
7. a high-pressure oil pump of engine, it is characterized in that, arranging electromagnetic valve in the oil suction chamber of described high-pressure oil pump, electromagnetic valve uses the combination type damping structure described in any one of claim 1-4, the spool (1) of combination type damping structure is controlled by solenoid, and is driven reset by back-moving spring；The axle journal (3-5) of the valve rod of combination type damping structure supports the centre bore of seat (4) through valve, valve block (5) is fixed in end, mobile by valve rod (3) band moving valve plate (5), close and open valve and support the oil inlet passage (4-4) on seat (4), it is achieved with the break-make of high pressure chest.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610417025.0A CN106014737A (en) | 2016-06-15 | 2016-06-15 | Combined type damping structure capable of meeting low NVH noise of high-pressure oil pump of GDI engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610417025.0A CN106014737A (en) | 2016-06-15 | 2016-06-15 | Combined type damping structure capable of meeting low NVH noise of high-pressure oil pump of GDI engine |
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| CN106014737A true CN106014737A (en) | 2016-10-12 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201610417025.0A Pending CN106014737A (en) | 2016-06-15 | 2016-06-15 | Combined type damping structure capable of meeting low NVH noise of high-pressure oil pump of GDI engine |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108071535A (en) * | 2016-11-14 | 2018-05-25 | 马涅蒂-马瑞利公司 | Fuel feed pump |
| CN109284582A (en) * | 2018-11-23 | 2019-01-29 | 重庆长安汽车股份有限公司 | A kind of vehicle body pitch damping glue lightweight optimizing method for disposing |
| CN110206670A (en) * | 2019-05-24 | 2019-09-06 | 浙江吉利控股集团有限公司 | Fuel pressure regulating valve, gasoline direct injection engine high-pressure fuel supply system and vehicle |
| CN111652342A (en) * | 2019-12-18 | 2020-09-11 | 中国船舶重工集团有限公司第七一0研究所 | Moving magnetic counting device for monitoring excitation of air gun |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4905640A (en) * | 1988-04-25 | 1990-03-06 | Robert Bosch Gmbh | Fuel injection pump |
| RU2122648C1 (en) * | 1996-05-13 | 1998-11-27 | Геннадий Федорович Кузнецов | Fuel injection pump delivery valve for internal combustion engine |
| JP2004211580A (en) * | 2002-12-27 | 2004-07-29 | Bosch Automotive Systems Corp | Valve for high flow fuel and fuel supply pump provide with the same |
| DE102004024282A1 (en) * | 2004-05-15 | 2005-12-01 | Robert Bosch Gmbh | Pump-nozzle unit for internal combustion engine has control valve operated by hydraulic intensifier with first intensifying piston provided with blind hole in which is guided and sealed second intensifying piston |
| KR20130010933A (en) * | 2011-07-20 | 2013-01-30 | 현대자동차주식회사 | A noise reduction structure of the high pressure fuel pump of the gdi engine |
| CN104948366A (en) * | 2015-07-17 | 2015-09-30 | 温州巴腾电子科技有限公司 | Direct injection high-pressure fuel pump |
| CN105484918A (en) * | 2015-12-06 | 2016-04-13 | 北京工业大学 | Oil return control method for unit pump fuel oil system |
-
2016
- 2016-06-15 CN CN201610417025.0A patent/CN106014737A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4905640A (en) * | 1988-04-25 | 1990-03-06 | Robert Bosch Gmbh | Fuel injection pump |
| RU2122648C1 (en) * | 1996-05-13 | 1998-11-27 | Геннадий Федорович Кузнецов | Fuel injection pump delivery valve for internal combustion engine |
| JP2004211580A (en) * | 2002-12-27 | 2004-07-29 | Bosch Automotive Systems Corp | Valve for high flow fuel and fuel supply pump provide with the same |
| DE102004024282A1 (en) * | 2004-05-15 | 2005-12-01 | Robert Bosch Gmbh | Pump-nozzle unit for internal combustion engine has control valve operated by hydraulic intensifier with first intensifying piston provided with blind hole in which is guided and sealed second intensifying piston |
| KR20130010933A (en) * | 2011-07-20 | 2013-01-30 | 현대자동차주식회사 | A noise reduction structure of the high pressure fuel pump of the gdi engine |
| CN104948366A (en) * | 2015-07-17 | 2015-09-30 | 温州巴腾电子科技有限公司 | Direct injection high-pressure fuel pump |
| CN105484918A (en) * | 2015-12-06 | 2016-04-13 | 北京工业大学 | Oil return control method for unit pump fuel oil system |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108071535A (en) * | 2016-11-14 | 2018-05-25 | 马涅蒂-马瑞利公司 | Fuel feed pump |
| CN108071535B (en) * | 2016-11-14 | 2021-05-28 | 马涅蒂-马瑞利公司 | Fuel supply pump |
| CN109284582A (en) * | 2018-11-23 | 2019-01-29 | 重庆长安汽车股份有限公司 | A kind of vehicle body pitch damping glue lightweight optimizing method for disposing |
| CN110206670A (en) * | 2019-05-24 | 2019-09-06 | 浙江吉利控股集团有限公司 | Fuel pressure regulating valve, gasoline direct injection engine high-pressure fuel supply system and vehicle |
| CN111652342A (en) * | 2019-12-18 | 2020-09-11 | 中国船舶重工集团有限公司第七一0研究所 | Moving magnetic counting device for monitoring excitation of air gun |
| CN111652342B (en) * | 2019-12-18 | 2023-09-01 | 中国船舶重工集团有限公司第七一0研究所 | Moving-magnet counting device for monitoring excitation of air gun |
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Application publication date: 20161012 |