CN202203014U - Low-viscosity fuel injector of diesel engine - Google Patents
Low-viscosity fuel injector of diesel engine Download PDFInfo
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- CN202203014U CN202203014U CN2011202748748U CN201120274874U CN202203014U CN 202203014 U CN202203014 U CN 202203014U CN 2011202748748 U CN2011202748748 U CN 2011202748748U CN 201120274874 U CN201120274874 U CN 201120274874U CN 202203014 U CN202203014 U CN 202203014U
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Abstract
The utility model relates to a low-viscosity fuel injector of a diesel engine. The low-viscosity fuel injector mainly comprises a fuel injector body, a needle valve, a needle valve body and a low-pressure-difference control valve. The low-viscosity fuel injector is characterized in that an annular decompression groove on a sliding fit surface of the needle valve and the needle valve body divides the fit clearance into a throttling decompression clearance and a low-pressure-difference lubrication clearance; the annular decompression groove is communicated with a pressure storage cavity on a low-pressure-difference valve through an oil duct; the middle part of the low-pressure-difference lubrication clearance is communicated with the low-pressure-difference control valve through a low-pressure-difference lubrication oil groove and an oil duct; and the low-pressure-difference control valve is communicated with a high-pressure lubrication oil interface through a lubrication oil duct. By adopting a micro clearance throttling decompression structure with the pressure storage cavity and a low-pressure-difference liquid seal and lubrication structure, the seal and lubrication of the sliding fit surface of the needle valve and a guide round hole are ensured, and the abrasion invalidity problem of the needle valve and the guide round hole when low-viscosity fuels are injected is overcome, thus the diesel engine can reliably burn low-viscocity alternative fuels such as dimethyl ether, methyl alcohol and the like.
Description
Technical field
The utility model belongs to technical field of internal combustion engines, specifically relate to a kind of can dimethyl ether fuel, the oil sprayer of multiple low-viscosity fuel such as methyl alcohol, ethanol.
Technical background
The diesel engine thermal efficiency is high, has become widely used motors such as automobile, tractor, engineering machinery, naval vessel, train.Use for diesel engine diesel oil is made fuel, reduces year by year owing to refine the petroleum resources of diesel oil in recent years, and countries in the world are all in the alternative fuel of seeking and promote diesel oil for this reason.Use for diesel engine positive injector dimethyl ether fuel discharging is superior to Europe III index, can reach Europe IV and Euro V emissions after adding exhaust gas recirculation.Countries in the world process development test generally acknowledges that the coal preparing dimethy ether is the clean fuel that substitutes diesel oil, and the alternative fuel that methyl alcohol test back affirmation methyl alcohol also can be made diesel oil is burnt with the Japanese igniting device that on diesel engine, adds by Germany.Because during the work of the injector nozzle matching parts of diesel injector; Rely on diesel fuel lubricity and sealing between needle-valve and the needle-valve body; (3～8Kg/ms) is little a lot, and needle-valve and needle-valve body wear and tear soon, fuel leak was lost efficacy because the fluid viscosity (being respectively 0.15Kg/ms and 0.6Kg/ms) of dimethyl ether and methyl alcohol is than diesel oil fluid viscosity when diesel engine dimethyl ether fuel or methyl alcohol.This problem is to hinder one of subject matter of on diesel engine, promoting low-viscosity fuels such as dimethyl ether fuel and methyl alcohol.
At present; The diesel engine overwhelming majority in usefulness still uses the mechanical type oil spout; Electronically controlled unit pump injection system newly developed also is to adopt positive injector; Innovation existing machinery formula oil sprayer addresses the above problem, and makes low viscosity alternative fuel such as existing diesel dimethyl ether fuel and reduces exhaust emission, is urgent problem in the art.
For addressing the above problem; A kind of lubricating fitting of dimethyl ether engine oil sprayer is disclosed for CN1599266Y like Chinese patent notice of authorization number; Be a kind of with high pressure gas holder through the outlet pressure regulator valve be connected with the large tank of lubricant oil pressurizing cylinder; The small piston that promotes in the small oil tank through the big piston in the large tank is pressed onto the lubricant oil supercharging in the small oil tank in the oil pocket of needle-valve fitting surface through pipeline; Play lubricated and seal action, this device exists and is difficult to long-term fuel feeding, particularly can not control the pressure reduction of lubricant oil and fuel oil; Needle-valve pressure end fuel oil is pressed in and reaches 700～1000bar when spraying; 0～20bar is only arranged when not spraying, and lubricant oil can flow into fuel oil and will form the burn oil phenomenon when the too high not oil spout of lubrication pressure, and low-viscosity fuel such as dimethyl ether can get into matching gap and makes the needle-valve wear out failure when lubricant oil forces down oil spout.Thereby this device does not have the instance of practical application so far.
And for example the Chinese patent publication number is that CN1275676A discloses a kind of low-pressure electric controlled dimethyl ether fuel injection system; It is a kind of device of the dimethyl ether in the dimethyl ether jar being sent into atomizer through ECU with the high pressure nitrogen of high-pressure nitrogen bottle; Still do not solve the problem of injector nozzle matching parts wear and leakage; And the system that the Chinese patent Granted publication disclosed diesel engine double-fuel oil pump that number is CN1312393C sprays two kinds of fuel; The scheme of injector nozzle matching parts wear problems when equally also not proposing to solve dimethyl ether fuel injection
The applicant's utility model patent (patent No. ZL2010 2 0586313.7) a kind of Electrocontrolled high-pressure common rail fuel injection apparatus has solved the lubricated and sealing problem of the little Electrocontrolled high-pressure common rail fuel injector needle valve coupling of fuel pressure fluctuation, but still can not solve the lubricated and sealing problem of needle-valve of the big positive injector of fuel pressure fluctuation.
Summary of the invention:
The purpose of the utility model is the problem of oil sprayer injector valve matching part abrasion, leakage failure when overcoming low viscosity alternative fuel such as above-mentioned diesel engine dimethyl ether fuel; Provide a kind of and do not rely on the lubricated and sealing injector valve idol part of fuel oil, and adopt the diesel engine low-viscosity fuel oil sprayer of microgap throttling buck configuration and low differential pressure liquid lubrication structure that the pressure accumulation chamber is arranged.
The utility model is to adopt following technological scheme to realize:
A kind of diesel engine low-viscosity fuel oil sprayer comprises oil injector body 1, needle-valve 2, needle-valve body 3, low differential pressure control valve 6.
Described needle-valve 2 is contained in the guiding circular hole K1 of needle-valve body 3 and with guiding circular hole K1 and is accurate being slidingly matched; The spring chamber K2 that is provided with in the described oil injector body 1 is communicated with the needle-valve guiding circular hole K1 of needle-valve body 3; Upper end with spring chamber K2 on described needle valve spring 5 is contained in the spring chamber K2 joins; The upper end of lower end and needle-valve 2 joins, and the conical surface M2 of needle-valve 2 lower ends is pressed in the upper end of nozzle opening R6 under the elastic force effect of needle valve spring 5, nozzle opening is sealed.Be characterized in: on the face that is slidingly matched of needle-valve 2 and the guiding circular hole K1 of needle-valve body 3, be provided with annular gas pressure relief slot x1, annular gas pressure relief slot x1 with needle-valve 2 and guiding circular hole K1 be slidingly matched separated for from annular gas pressure relief slot x1 down to the throttling step-down gap J1 of annular pressure chamber R4, from annular gas pressure relief slot x1 upwards to the lubricated microgap J2 of the low differential pressure of spring chamber K2; Annular gas pressure relief slot x1 is communicated with low differential pressure control valve 6 or is communicated with low differential pressure control valve 6 and spring chamber k2 respectively through pressure release oil duct x2, threeway pressure accumulation oil duct x3T through pressure release oil duct x2, pressure accumulation oil duct x3; The middle part of J2 is provided with annular low pressure difference oil groove r5 in the low differential pressure lubrication gap, and annular low pressure difference oil groove r5 is communicated with low differential pressure control valve 6 through oil leab r4, low differential pressure oil leab r3; Low differential pressure control valve 6 is communicated with high-tension lubrication tubing interface r1 through high-tension lubrication oil duct r2.
The beneficial effect of the utility model:
A kind of diesel engine low-viscosity fuel of the utility model oil sprayer adopts microgap throttling buck configuration and low differential pressure liquid seal and the lubricating structure that the pressure accumulation chamber is arranged; The problem and the lubricated problem of needle-valve of fuel leakage have been solved effectively; Avoided diesel engine machinery formula oil sprayer injector valve to contact with guiding the direct of circular hole; Guaranteed needle-valve and the sealing of the face that is slidingly matched of the precision of the circular hole that leads and lubricated; When having overcome the injection low-viscosity fuel, the problem of fuel leakage and needle-valve and guiding circular hole wear out failure makes diesel oil function low viscosity such as dimethyl ether fuel, methyl alcohol alternative fuel reliably.
Description of drawings:
Fig. 1 is the structural representation of first embodiment of a kind of diesel engine low-viscosity fuel of the utility model oil sprayer
Fig. 2 is the structural representation of second embodiment of a kind of diesel engine low-viscosity fuel of the utility model oil sprayer
Among Fig. 1 and Fig. 2: 1, oil injector body; 2, needle-valve; 3, needle-valve body; 4, needle-valve body tightening nut; 5, needle valve spring; 6, low differential pressure control valve; 7, tightening nut; R1, fuel pipe interface; R2, fuel oil road; R3, following fuel oil road; R4, annular pressure chamber; R5, annular fuel oil road; R6, nozzle opening; Conical surface under M1, the needle-valve; M2, needle-valve lower end conical surface; K1, guiding circular hole; K2, spring chamber; K3, pressure accumulation chamber; K4, low differential pressure oil pocket; X1, annular gas pressure relief slot; X2, pressure release oil duct; X3, pressure accumulation oil duct; X4, last pressure accumulation oil duct; R1, high-tension lubrication tubing interface; R2, high-tension lubrication oil duct; R3, low differential pressure oil leab; R4, oil leab; R5, annular low pressure difference oil groove; J1, throttling step-down gap; J2, low differential pressure lubrication gap; J3, annular micro-gap; 6.1, oil cylinder; 6.2, equilibrated valve, 6.3, low differential pressure spring; 6.4 valve opening; 6.5, annular high-tension lubrication oil groove; 6.6, go up the high-tension lubrication oil duct; H1, return tube interface; H2, back oil road; X3T, threeway pressure accumulation oil duct,
Embodiment
Further describe below in conjunction with the embodiment of accompanying drawing the utility model.
The structural representation of the utility model first embodiment as shown in Figure 1.A kind of diesel engine low-viscosity fuel oil sprayer comprises oil injector body 1, needle-valve 2, needle-valve body 3, needle-valve body tightening nut 4, needle valve spring 5, low differential pressure control valve 6.Wherein: the low differential pressure control valve is mechanical type (or electric-controlled type).
Described oil injector body 1 is provided with fuel pipe interface R1, and following fuel oil road R3, the annular pressure chamber R4 of fuel pipe interface R1 in fuel oil road R2, needle-valve body 3 is connected with annular fuel oil road R5.
Described needle-valve 2 is contained in the guiding circular hole K1 of needle-valve body 3, and with the microgap ringwise that is slidingly matched of the precision of guiding circular hole K1, its matching gap is in 0.0015～0.0025mm scope; The spring chamber K2 that the lower end of oil injector body 1 is provided with is communicated with the needle-valve of needle-valve body 3 guiding circular hole K1; Upper end with spring chamber K2 on described needle valve spring 5 is contained in the spring chamber K2 joins; The lower end is connected with the upper end of needle-valve 2; Needle-valve lower end conical surface M2 is pressed in the upper end of nozzle opening R6 under the elastic force effect of needle valve spring 5, and with nozzle opening R6 sealing, spring chamber K2 is communicated with return tube interface H1 through back oil road H2; Described low differential pressure control valve 6 comprises that oil cylinder 6.1, length are 30 millimeters equilibrated valve 6.2, low differential pressure spring 6.3; Equilibrated valve 6.2 is contained in the oil cylinder 6.1 oil cylinder 6.1 is divided into the pressure accumulation chamber k3 of upper end, the low differential pressure oil pocket k4 of lower end; The micro-gap J3 ringwise that is slidingly matched of the precision of equilibrated valve 6.2 and oil cylinder 6.1; Its matching gap is 0.0015～0.0025 millimeter scope; On the fitting surface of the oil cylinder 6.1 that cooperates with equilibrated valve 6.2, be provided with annular high-tension lubrication oil groove 6.5, annular high-tension lubrication oil groove 6.5 is connected with high-tension lubrication tubing interface r1 through last high-tension lubrication oil duct 6.6, high-tension lubrication oil duct r2; The upper-end surface of equilibrated valve 6.2 is connected with the lower end of low differential pressure spring 6.3, and the upper end of low differential pressure spring 6.3 is connected with the last end face of oil cylinder 6.1; Receive the 6.3 elastic force effects of low difference spring; The lower end of equilibrated valve 6.2 is pressed on the lower end surface of oil cylinder 6.1; Valve opening 6.4 in the equilibrated valve 6.2 is communicated with low differential pressure oil pocket k4, and equilibrated valve 6.2 its valve opening 6.4 when this position is connected with annular high-tension lubrication oil groove 6.5; Low differential pressure oil pocket k4 is connected with low differential pressure oil groove r5 through low differential pressure oil duct r3, oil leab r4.
On the face that is slidingly matched of needle-valve 2 and the guiding circular hole K1 of needle-valve body 3, be provided with annular gas pressure relief slot x1, annular gas pressure relief slot x1 with the separated that is slidingly matched of needle-valve 2 and guiding circular hole K1 for from annular gas pressure relief slot x1 upwards being 30 millimeters low differential pressure lubrication gap J2 to the length of spring chamber K2 down to the throttling step-down gap J1 of annular pressure chamber R4, from annular gas pressure relief slot x1; Annular gas pressure relief slot x1 is connected with pressure accumulation chamber k3 through pressure release oil duct x2, pressure accumulation oil duct x3, last pressure accumulation oil duct x4; On the guiding circular hole face at the middle part of low differential pressure lubrication gap J2, be provided with annular low pressure difference oil groove r5; The middle part of low differential pressure lubrication gap J2 is communicated with the low differential pressure oil pocket k4 of low differential pressure control valve 6 through annular low pressure difference oil groove r5, oil leab r4, low differential pressure oil leab r3; The last high-tension lubrication oil duct 6.6 of low differential pressure control valve 6 is communicated with high-tension lubrication tubing interface r1 through high-tension lubrication oil duct r2.
The structural representation of second embodiment of the utility model as shown in Figure 2; Its claimed structure only has two places different with the structure of first embodiment of the utility model shown in Figure 1, and 1, annular gas pressure relief slot x1 is communicated with the last pressure accumulation oil duct x4 and the pressure accumulation chamber K3 of spring chamber K2 and low differential pressure control valve 6 respectively through pressure release oil duct x2, threeway pressure accumulation oil duct x3T; 2, spring chamber K2 does not have back oil road H2 and return tube interface H1.
The working principle of a kind of diesel engine low-viscosity fuel of the utility model oil sprayer first embodiment structure:
The diesel engine low-viscosity fuel fuel injector structure of the utility model as shown in Figure 1; Diesel engine prepare to start high pressure fuel pump also during pump oil; In the high-tension lubrication oil pipe pressure be the 180bar high pressure lubricant oil from high-tension lubrication tubing interface r1 through high-tension lubrication oil duct r2, go up high-tension lubrication oil duct 6.6, annular high-tension lubrication oil groove 6.5, valve opening 6.4 and get into low differential pressure oil pocket k4; Promote equilibrated valve 6.2 up compression and low pressure difference springs 6.3; When 6.4 risings of the valve opening on the equilibrated valve 6.2 were broken off with being communicated with of annular high-tension lubrication oil groove 6.5; Extreme pressure lubricant stops to get into low differential pressure oil pocket k4; 6.3 this moments of set low differential pressure spring are 0.5bar to the oil pressure that the elastic force of equilibrated valve 6.2 produces in low differential pressure oil pocket k4, because the middle part of low differential pressure lubrication gap J2 is communicated with low differential pressure oil pocket k4 through annular low pressure difference oil groove r5, oil leab r4, low differential pressure oil leab R3, at this moment; Lubricating oil pressure among the J2 of low differential pressure lubrication gap is 0.5bar, and the oil pressure among the annular gas pressure relief slot x1 is 0; Test confirms that length is 15 millimeters; The gap is that lubricant oil in 0.0015～0.0025 millimeter the annular microgap is when pressure reduction is less than 200bar at the two ends, gap; Lubricant oil in the gap does not have flow phenomenon; Lubricant oil among the J2 of low differential pressure lubrication gap can not flow into annular gas pressure relief slot x1 and spring chamber k2, and the fuel oil among the annular gas pressure relief slot x1 can not flow into low differential pressure lubrication gap J2 yet; Extreme pressure lubricant in the annular high-tension lubrication oil groove 6.5 can not flow into pressure accumulation chamber k3 and low differential pressure oil pocket k4 from annular micro-gap J3 yet.
The fuel pressure P1 oil sprayer oil spout that sharply raises in high pressure fuel pump pump when oil high-pressure oil pipe interface R1: high pressure fuel is through fuel pipe interface R1, fuel oil road R2, fuel oil road R3 gets into annular pressure chamber R4 and ring shaped oil passage R5 down; Conical surface M1 is upwarded pressure greater than the downward power of 5 pairs of needle-valves of needle valve spring 2 by fuel oil under the needle-valve; Needle-valve 2 upwards rises; Needle-valve lower end conical surface M2 lifts away from the upper end-hole of nozzle opening R6; High pressure fuel sprays from nozzle opening R6; Maximum spout oil pressure P1max reaches 700bar～1500bar during oil spout, meanwhile, the oil pressure among the annular pressure chamber R4 be the P1max high pressure fuel through small annular throttling step-down gap J1 leak into annular gas pressure relief slot x1, because the small throttling hypotensive effect that throttling step-down gap J1 is arranged; Leak into fuel oil that oil pressure among the annular gas pressure relief slot x1 is reduced to P2 through pressure release oil duct x2, pressure accumulation oil duct x3, go up pressure accumulation oil duct x4 and get into the air among the pressure accumulation chamber K3 compression pressure accumulation chamber K3; Each oil spout all has fuel oil to leak into pressure accumulation chamber K3, and the pressure P 2 among annular gas pressure relief slot x1 and the pressure accumulation chamber K3 raises with the amount of fuel increase that leaks in the high frequency injection process, raises with P2; The pressure reduction of oil pressure P2 among the annular pressure chamber R4 among injection pressure P1max and the annular gas pressure relief slot x1 reduces, and leaks into the fuel amount of the leaking into Q of pressure accumulation chamber K2 during each oil spout
XReduce with the P2 rising; During diesel engine running work, each oil spout Tp perdurabgility suspends injection time T 5 °～18 ° crank angle range between per twice oil spout
H715 °～702 ° crank angle range, than oil spout (draining) time T
X143～39 times of length, i.e. T
H=143～39T
XSuspend injection time T
HIn; Fuel pressure P1min ≈ 0～20bar among the annular pressure chamber R4 (adopting the Injection Pump that throttle orifice is arranged in the outlet valve); Fuel oil among the K3 of pressure accumulation chamber is let out the winding shape R4 of pressure chamber through last pressure accumulation oil duct x4, pressure accumulation oil duct x3, pressure release oil duct x2, annular gas pressure relief slot x1, throttling step-down gap J1, and its fuel oil of letting out back the R4 of pressure chamber amount of letting out back is Q
H, raising with pressure P among pressure accumulation chamber K3 and the annular gas pressure relief slot x1 2, fuel oil is let out back amount Q
HIncrease, and leak into the amount of fuel Q of pressure accumulation chamber K3
XReduce along with the rising of pressure P 2 among the K3 of pressure accumulation chamber, R4 leaks into the amount of fuel Q of annular gas pressure relief slot x1 through throttling step-down gap J1 from the pressure chamber
XWith the amount of fuel Q that lets out back the R4 of pressure chamber from annular gas pressure relief slot x1 through throttling step-down gap J1
HWhen equating,, Q
H=Q
X, oil pressure P2 is the flow equilibrium oil pressure among pressure accumulation chamber K3 and the annular gas pressure relief slot x1, experimental measurement balance oil pressure P2＜100bar at this moment.
Annular pressure chamber R4 through throttling step-down gap J1 link to each other with annular gas pressure relief slot x1, annular gas pressure relief slot x1 through pressure release oil duct x2, pressure accumulation oil duct x3, go up the throttling step-down that pressure accumulation oil duct x4 is communicated with pressure accumulation chamber K3 and the structure of voltage stabilizing, the pressure reduction that makes oil pressure P2 peak and pressure surge in the gas pressure relief slot is less than oil pressure peak among the annular pressure chamber R4 and pressure surge pressure reduction.
During the oil sprayer oil spout; Raise with pressure accumulation chamber k3 intermediate fuel oil pressure P 2; It is descending that the fuel pressure of equilibrated valve 6.2 upper ends and the elastic force of spring 6.3 promote equilibrated valve 6.2; When the valve opening on the equilibrated valve 6.2 6.4 is communicated with annular high-tension lubrication oil groove 6.5; Extreme pressure lubricant gets into low differential pressure oil pocket k4 from annular high-tension lubrication oil groove 6.5 through valve opening 6.4; Oil pressure P4 among the low differential pressure oil pocket k4 raises; At this moment, the lubricating oil pressure that acts on equilibrated valve 6.2 lower ends is greater than the elastic force of the low differential pressure spring 6.3 of upper end and making a concerted effort of fuel pressure P2, and the valve opening 6.4 of the up compression and low pressure difference of equilibrated valve spring 6.3 to equilibrated valve 6.2 breaks off with being communicated with of annular high-tension lubrication oil groove 6.5 and stops into extreme pressure lubricant; The elastic force of 6.3 this moments of the low differential pressure spring selected for use acts on the oil pressure that equilibrated valve 6.2 produces in low differential pressure oil pocket k4 be 0.5bar; P4=P2+0.5bar, promptly among the low differential pressure oil pocket k4 lubricating oil pressure P4 than the high 0.5bar of fuel pressure P2 among pressure accumulation oil pocket k3 and the annular gas pressure relief slot x1, when the oil pressure among the low differential pressure oil pocket k4 descends; It is descending that fuel pressure P2 among the k3 of pressure accumulation chamber and low differential pressure spring 6.3 promote equilibrated valve 6.2; Valve opening 6.4 is communicated with high pressure annular oil groove 6.5 again, extreme pressure lubricant again from high pressure annular oil groove 6.5 through valve opening 6.4, get into low differential pressure oil pocket k4 and promote equilibrated valve 6.2 and go upward to valve opening 6.4 and high-tension lubrication oil groove 6.5 and break off and stop that oil pressure P4 reaches P2+0.5bar oil-feed, the low differential pressure oil pocket k4, promptly till the P4=P2+0.5bar; Lubrication pressure P4 among the low differential pressure control valve 6 control low differential pressure oil pocket k4 reaches the middle part of low differential pressure lubrication gap J2, the lubricating oil pressure P4=P2+0.5bar among the J2 of low differential pressure lubrication gap through low differential pressure oil leab r3, oil leab r4, annular low pressure difference oil groove r5; The lubricating oil pressure P2 at low differential pressure control valve 6 control low differential pressure lubrication gap J2 middle parts is than the high 0.5bar of fuel pressure P4 among the annular gas pressure relief slot x1; Stoped the fuel oil among the annular gas pressure relief slot x1 to get into gap J2, overcome the fuel leakage problem effectively, the lubricant oil among the J2 of low differential pressure lubrication gap can not flow into annular gas pressure relief slot x1 yet; The micro lubricating oil of J2 infiltration spring chamber k2 flows back to lubricating oil tank through back oil road H2, return tube interface H1 from the low differential pressure lubrication gap in oil sprayer long-time continuous injection process; Lubricant film among the J2 of low differential pressure lubrication gap floats in guiding circular hole K1 needle-valve 2; Avoided direct the contacting of needle-valve 2 with guiding circular hole K1; Guaranteed the face that is slidingly matched lubricated of needle-valve 2 and the precision of guiding circular hole, overcome the problem of needle-valve 2 with guiding circular hole K1 wear out failure.
The groundwork principle of the groundwork principle of the second embodiment structure of the utility model and the first embodiment structure of the utility model is basic identical; Difference is that the second embodiment structure of the utility model does not have back oil road H2 and return tube interface H1; Its spring chamber K2 is communicated with annular gas pressure relief slot x1 through threeway pressure accumulation oil duct x3T, pressure release oil duct x2; Thereby spring chamber K2 has the pressure accumulation effect; Oil pressure P2 wherein equates with oil pressure P2 among the annular gas pressure relief slot x1; Than the low 0.5bar of lubricating oil pressure at low differential pressure lubrication gap J2 middle part, thereby the fuel oil that leaks among annular gas pressure relief slot x1 and the spring chamber K2 can not leak into low differential pressure lubrication gap J2, solved the lubrication problem of fuel leakage problem and needle-valve 2 and the circular hole K1 that leads effectively.
A kind of diesel engine low-viscosity fuel of the utility model oil sprayer has solved the sealing problem and the lubrication problem of oil-fuel injector needle-valve when using low-viscosity fuel and guiding circular hole, makes diesel oil function low-viscosity fuel such as dimethyl ether fuel, methyl alcohol reliably.
Claims (1)
1. a diesel engine low-viscosity fuel oil sprayer comprises oil injector body (1), needle-valve (2), needle-valve body (3), needle-valve body tightening nut (4), spring (5), low differential pressure control valve (6); Described needle-valve (2) is contained in the guiding circular hole (K1) of needle-valve body (3) and with guiding circular hole (K1) and is accurate being slidingly matched; The spring chamber (K2) that is provided with in the described oil injector body (1) is communicated with the needle-valve of needle-valve body (3) guiding circular hole (K1); Upper end with spring chamber (K2) on described needle valve spring (5) is contained in the spring chamber (K2) joins; The upper end of lower end and needle-valve (2) joins, and the conical surface (M2) of needle-valve (2) lower end is pressed in the upper end of nozzle opening (R6) and nozzle opening is sealed under the elastic force effect of needle valve spring (5); It is characterized in that: on the face that is slidingly matched of the guiding circular hole (K1) of described needle-valve (2) and needle-valve body (3), be provided with annular gas pressure relief slot (x1), described annular gas pressure relief slot (x1) with needle-valve (2) and guiding circular hole (K1) be slidingly matched separated for from annular gas pressure relief slot (x1) down to the throttling step-down gap (J1) of annular pressure chamber (R4) and from annular gas pressure relief slot (x1) upwards to the low differential pressure lubrication gap (J2) of spring chamber (K2); Its annular gas pressure relief slot (x1) is communicated with low differential pressure control valve (6) through pressure release oil duct (x2), pressure accumulation oil duct (x3), or is communicated with low differential pressure control valve (6) and spring chamber (K2) respectively through pressure release oil duct (x2), threeway pressure accumulation oil duct (x3T); Also be provided with annular low pressure difference oil groove (r5) at the middle part of described low differential pressure lubrication gap (J2), annular low pressure difference oil groove (r5) is communicated with low differential pressure control valve (6) through oil leab (r4), low differential pressure oil leab (r3); Described low differential pressure control valve (6) is communicated with high-tension lubrication tubing interface (r1) through high-tension lubrication oil duct (r2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202748748U CN202203014U (en) | 2011-07-30 | 2011-07-30 | Low-viscosity fuel injector of diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202748748U CN202203014U (en) | 2011-07-30 | 2011-07-30 | Low-viscosity fuel injector of diesel engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202203014U true CN202203014U (en) | 2012-04-25 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011202748748U Expired - Lifetime CN202203014U (en) | 2011-07-30 | 2011-07-30 | Low-viscosity fuel injector of diesel engine |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102322378A (en) * | 2011-07-30 | 2012-01-18 | 郑国璋 | Low-viscosity fuel injector of diesel engine |
-
2011
- 2011-07-30 CN CN2011202748748U patent/CN202203014U/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102322378A (en) * | 2011-07-30 | 2012-01-18 | 郑国璋 | Low-viscosity fuel injector of diesel engine |
| CN102322378B (en) * | 2011-07-30 | 2013-03-27 | 郑国璋 | Low-viscosity fuel injector of diesel engine |
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