CN202832919U - Pressure regulation timing advance device - Google Patents
Pressure regulation timing advance device Download PDFInfo
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- CN202832919U CN202832919U CN 201220291460 CN201220291460U CN202832919U CN 202832919 U CN202832919 U CN 202832919U CN 201220291460 CN201220291460 CN 201220291460 CN 201220291460 U CN201220291460 U CN 201220291460U CN 202832919 U CN202832919 U CN 202832919U
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- 230000033228 biological regulation Effects 0.000 title claims abstract description 32
- 239000003921 oil Substances 0.000 claims abstract description 155
- 239000000295 fuel oil Substances 0.000 claims abstract description 17
- 238000007789 sealing Methods 0.000 claims abstract description 4
- 239000002828 fuel tank Substances 0.000 claims description 8
- 239000011148 porous material Substances 0.000 claims description 7
- 229910000831 Steel Inorganic materials 0.000 claims description 3
- 239000007788 liquid Substances 0.000 claims description 3
- 239000010959 steel Substances 0.000 claims description 3
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- 230000001105 regulatory effect Effects 0.000 abstract 1
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- 230000009471 action Effects 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
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- 230000007812 deficiency Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
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- 230000000977 initiatory effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
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Abstract
The utility model provides a pressure regulation timing advance device which comprises a pump body, a pump cover, an oil delivery pump, a pressure regulating valve small hole, a hydraulic time corrector, an oil return solenoid valve and a cold boot flame jetting oil supply device. The oil delivery pump is arranged in the pump body which is communicated with the pump cover in a sealing mode, and the oil return solenoid valve penetrates through an oil pipe assembly of a cold boot flame preheating oil supply device and is connected with the pump cover. Reasonable assembly is adopted to form a novel combination, and the combination effect greatly improves intrinsic characteristics of oil supply time correction advance of an original VE type high pressure fuel oil injection pump, and the rotation speed of a low speed advancer to function is greatly reduced, advance amount is effectively improved, high speed advance amount is effectively reduced, combustion conditions in different rotation speeds are improved, and a diesel engine of an existing lightweight car meets requirements of national emission III standards.
Description
Technical field
The utility model relates to oil pump technology field, particularly the employed pressure regulation timing of a kind of VE type distribution type jerk pump advancer.
Background technique
Altogether the rail fuel oil supply system has obtained internationally recognized at present as Fuel Feeding System for Diesel Engine leading.The pump line mouth system used with the conventional diesel engine fuel supply system compares, and is total to one of the most outstanding advantage of rail fuel oil supply system and just is that it is so-called pressure time Flexible Control that its jet pressure, discharge time can arrange arbitrarily within the specific limits according to demand.This outstanding advantage makes it can be according to the performance of diesel engine and the demand of discharging, be optimized with ideal injection pressure and injection time parameter from the fuel delivery of high rotating speed up to each rotating speed that starts rotating speed, final so that the power character of diesel engine is not fully exerted, economic index is good, and discharging also reaches relevant criterion.
Fuel feeding is one of key technology scheme that reaches at present national light-duty vehicle discharging III standard-required timely and accurately for the fuel supply system jerk pump.
And pump line mouth supply system is along with the reduction of rotating speed, the reduction of oil mass, and the pump end pressure decreases, and jet pressure also decreases.Aspect dynamically fuel feeding shifts to an earlier date, because normal operation is the centrifugal mechanical advancing device, along with the reduction centrifugal force of rotating speed also decreases, cause its dynamic fuel feeding also to reduce in advance thereupon.
For the VE pump, because what use is the hydraulic pressure advance mechanism that is contained in pump body, descending with the oil transportation ability of the reduction vane fuel supply pump of rotating speed causes pump chamber pressure to reduce with rotating speed to reduce, so that dynamically fuel supply advance angle also reduces along with the reduction of rotating speed.This drawback becomes one of maximum shortcoming that pump line mouth system can't compare with common rail system, and this shortcoming is along with improving constantly of emission request also seems more outstanding.Be embodied in following two aspects.
First aspect is; The pump chamber pressure of low speed is low.
Along with improving constantly of exhaust index, in order to satisfy the exhaust index of the high rotating speed operating mode of diesel engine, one of technology that adopts at present is exactly that the static fuel supply advance angle of diesel engine is constantly reducing, and initiating combustion is constantly close to top dead center.This trend is but in advance opposite with diesel engine required fuel feeding when the low speed.Be in the cold start-up stage of low temperature, low speed, warm-up phase after starting to be transitioned on the acceleration performance in normally travelling at diesel engine, because the characteristics of above-mentioned operating mode are that cylinder temperature is low, rotating speed is low, induction air flow ratio is low, the combustion gas mixing quality is relatively relatively poor, in addition because the low jet pressure that causes of rotating speed is low so that the injection delivery angle is relatively large, combustion condition is perfect not, be easy to cause this one-phase power character economic index poor, acceleration is bad, the shortcoming that discharge quality is poor.
Fuel pump for state's III standard, because static fuel supply advance angle is very little, so very unfavorable for the burning of diesel engine slow-speed of revolution operating mode tissue, so require the dynamic fuel feeding rotating speed that works in advance more early better, what slow-speed of revolution section advancing device stroke was carried is the bigger the better sooner, the loss that reduces to remedy static fuel supply advance angle is for power character, Economy and the discharging that improves low speed segment contributes.
In order to achieve the above object, just must manage to improve the pump chamber pressure of the low speed segment of VE type proportioning pump.
Second aspect is; It is too fast that high regime is carried.
Along with improving constantly of exhaust index, in order to satisfy the exhaust index of the high rotating speed operating mode of diesel engine, the dynamic advancement amount of two diesel engine high regime of the technology that adopts at present also will reduce.
Fuel pump for state's III standard, high combustion pressure of explosion and maximum combustion temperature for strict its high regime of control, its dynamic fuel supply advance angle high regime need to carry slow, satisfying state's 3 effluent standard needs, so relatively formerly require mild many of high regime advancing device curve.
It is relatively slow that the high rotating speed that makes is carried, just must require the mild demand of tendency to satisfy high regime advancing device stroke by the larger advance device spring of design rigidity for reaching this target, the problem of bringing thus is because advance device spring rigidity is larger, the lowspeed pump cavity pressure is not enough to push away motionless advancing device, and the slow-speed of revolution is inoperative to be that the advancing device rotating speed hysteresis stroke that works is inadequate.Solution is to manage to improve pump chamber pressure as far as possible, does not do the unique channel that improves pump chamber pressure under the prerequisite of change at other component and reduces exactly recirculating oil quantity, and its prerequisite is not affect the oil pump recirculating oil quantity to guarantee that oil pump is in high-revolving normal heat radiation.
Oil return solenoid valve basic structure of the prior art its essence is a solenoid valve as shown in Figure 3, and coil, armature, spring and guiding valve are housed in the valve body.Solenoid valve energising when diesel engine is in startup and slow-speed of revolution section, armature overcomes spring force guiding valve is picked up, the guiding valve that picks up covers 4 apertures 11 in oil return solenoid valve top, cut off the oil return of oil return solenoid valve top 4 apertures 11, only have the oil return of 1 aperture 12 in bottom to get back to oil outlet tube, recirculating oil quantity reduces, and pump chamber pressure sharply raises, the demand that dynamic timing shifts to an earlier date when having satisfied pump start and slow-speed of revolution section.Be in normal operation during operating mode during the solenoid valve no electric circuit at diesel engine, pressure fuel oil from pump chamber is got back to oil outlet tube by the oil return of 4 apertures 11 in oil return solenoid valve top and 1 aperture 12 in bottom, this moment high while of rotating speed recirculating oil quantity is also large, satisfies simultaneously the demand that diesel engine dynamically shifts to an earlier date fuel feeding and oil pump heat radiation.Because its low speed rotating speed height that works, the high speed advancement amount is large so oil return solenoid valve only uses is requiring on the supporting VE type proportioning pump of low diesel engine for automobile without emission request or discharging standards.
The intrinsic timing of VE type jerk pump of the prior art shifts to an earlier date its shortcoming of characteristic and is: because the lowspeed pump cavity pressure is low, the timing rotating speed height that works in advance that is to say that slow-speed of revolution section is inoperative.In case timing is worked in advance, then along with the high speed stage of increase of the raising of rotating speed, pump chamber pressure carry again too fast.This intrinsic timing shifts to an earlier date characteristic and runs counter to the demand that existing light vapor diesel engine for automobile satisfies country's discharging III standard.
In order to have overcome above-mentioned shortcoming, adapt to the requirement of national associated drain rule, be necessary to propose a kind of new pressure regulation timing advancer.
The model utility content
The purpose of this utility model is to overcome above-mentioned deficiency, thereby a kind of pressure regulation timing advancer is provided, and has improved the combustion condition of different rotating speeds, has satisfied the demand of the national discharging of existing light vapor diesel engine for automobile III standard.
The technological scheme that the utility model adopts specifically is achieved in that
The utility model provides a kind of pressure regulation timing advancer, comprise the pump housing, pump cover, oil transfer pump, hydraulic pressure sharp time unit, pressure regulator valve aperture, oil return solenoid valve and cold-start flame-preheating oil feeding device, described oil transfer pump is contained in the described pump housing, the described pump housing becomes sealing to connect with described pump cover, connect through described pressure regulator valve aperture and described oil return solenoid valve, described oil return solenoid valve passes described cold-start flame-preheating oil feeding device oil pipe assembly and is connected with described pump cover.
Preferably, described oil return solenoid valve is two hole oil return solenoid valves, and the above has an oil outlet, and the below has an oil outlet.
Preferably, the oil outlet diameter above the described oil return solenoid valve is 0.8mm, and following oil outlet diameter is 0.5mm.
Preferably, described cold-start flame-preheating oil feeding device comprises oil connection, the first return tube, the second return tube, oil outlet tube, the external fuel tank of one end of described the first return tube, one end of described the second return tube is communicated with described oil connection, the external injector assembly of the other end, described oil outlet tube leads to the flame preheat main body.
Preferably, described oil return solenoid valve passes described oil returning pipe joint mesopore and is connected with described pump cover.
Preferably, described cold-start flame-preheating oil feeding device also comprises hydraulic oil-returning valve and transport pipe, one end of described hydraulic oil-returning valve is communicated with described transport pipe, and the other end is communicated with described the first return tube, and fuel oil flows into described cold-start flame-preheating oil feeding device by described oil return solenoid valve.
Preferably, described hydraulic oil-returning valve is for only to allow liquid to be flowed to the one-way valve of fuel tank by described oil connection.
Preferably, during described pressure regulation timing advancer work, the pressure fuel oil will flow into described oil return solenoid valve by the described pump housing, described pump cover, flow into described cold-start flame-preheating oil feeding device through described oil return solenoid valve again.
Preferably, described hydraulic pressure sharp time unit comprises piston of timing advance device, advance device spring, roller seat pin, balance staff, roller, roller base, the upper end of described roller seat pin is inserted into and is arranged in the described roller base that described roller is equipped with in the top, and the lower end vertically is inserted in the described balance staff; Described balance staff vertically is inserted into described piston of timing advance device middle part; Described piston of timing advance device horizontal setting consists of sliding pair with distributing the pump housing, and its two ends form the first space that communicates with pump housing hyperbaric chamber and the second space that communicates with pump housing low-pressure cavity with the described pump housing respectively; Advance device spring between piston of timing advance device and the pump housing is housed in the described second space.
Preferably, the steel wire diameter scope of described advance device spring is 2.98mm-3.02mm, and the overall length scope is 33.5mm-34.5mm, and range in stiffness is 69.3N/mm-78.3N/mm, and the spring outer diameter scope is 15.75mm-16.25mm.
Preferably, described piston of timing advance device overall length is 58mm-59mm, and described high voltage terminal comprises throttling pore and the screw of magnetic cylinder is installed that described low voltage terminal comprises the advance device spring mounting hole.
Preferably, described throttling pore diameter range is 0.47mm-0.55mm.
Pressure regulation timing advancer of the present utility model, the structure configuration rationally, rotating speed greatly reduces so that slow-speed of revolution advancing device works, advancement amount effectively improves, the high speed advancement amount is effectively reduced, improve the combustion condition of different rotating speeds, satisfied the demand of the national discharging of existing light vapor diesel engine for automobile III standard.
Description of drawings
Fig. 1 is the pressure regulation timing advancer main components scheme of installation of the utility model specific embodiment;
Fig. 2 is the outside schematic representation that links of pump cover, oil return solenoid valve, the cold-start flame-preheating oil feeding device of the utility model specific embodiment;
Fig. 3 is oil return solenoid valve (i.e. five hole oil return solenoid valves) the external structure schematic representation of prior art;
Fig. 4 is oil return solenoid valve (i.e. two hole oil return solenoid valves) the external structure schematic representation of the utility model specific embodiment;
Fig. 5 is the oil return solenoid valve internal structure schematic representation of the utility model specific embodiment;
Fig. 6 is the cold-start flame-preheating oil feeding device oil pipe assembly schematic representation of the utility model specific embodiment;
Fig. 7 is the hydraulic pressure sharp time unit internal structure schematic representation of the utility model specific embodiment;
Fig. 8 is the piston of timing advance device structural representation of the utility model specific embodiment;
Fig. 9 is the throttling pore structural representation of the utility model specific embodiment;
Figure 10 is the former timing mechanism of the utility model specific embodiment and pressure, the stroke curve comparison diagram of existing pressure regulation timing advancer.
Embodiment
For above-mentioned purpose of the present utility model, feature and advantage can be become apparent more, below in conjunction with accompanying drawing embodiment of the present utility model is described in detail, it will be more clear making above-mentioned and other purpose of the present utility model, Characteristics and advantages.Reference character identical in whole accompanying drawings is indicated identical part.Deliberately do not draw in proportion accompanying drawing, focus on illustrating purport of the present utility model.
Specific embodiment below in conjunction with Fig. 1-10 pair of pressure regulation timing advancer of the present utility model is elaborated.
As shown in Figure 1 and Figure 2, pressure regulation timing advancer of the present utility model comprises the pump housing 10, pump cover 20, oil transfer pump 30, hydraulic pressure sharp time unit 40, pressure regulator valve aperture 50, oil return solenoid valve 60 and cold-start flame-preheating oil feeding device 70.Oil transfer pump 30 is contained in the pump housing 10,20 one-tenth sealings of the pump housing 10 and pump cover connect, connect through pressure regulator valve aperture 50 and oil return solenoid valve 60, the oil returning pipe joint mesopore that oil return solenoid valve 60 passes cold-start flame-preheating oil feeding device 70 oil pipe assemblies is connected with pump cover 20.
Such as Fig. 4, shown in Figure 5, in the utility model, oil return solenoid valve 60 is two hole oil return solenoid valves, and the above has an oil outlet 13, and the below has an oil outlet 14.Oil outlet 13 diameters above the oil return solenoid valve 60 are 0.8mm, and following oil outlet 14 diameters are 0.5mm.
In the utility model, the job description of pressure regulation timing advancer: diesel engine is in case start, at once the pressure fuel oil that produces will flow into oil return solenoid valve 60 by the pump housing 10, pump cover 20, flow into cold-start flame-preheating oil feeding device 70 oil pipe assemblies through oil return solenoid valve 60 again, the demand for control according to different operating modes flows to respectively the flame preheat fuel outlet or flows to fuel-tank outlet again.
As shown in Figure 6, cold-start flame-preheating oil feeding device 70 of the present utility model comprises oil connection 1, the first return tube 5, the second return tube 3, oil outlet tube 2, the external fuel tank of one end of the first return tube 5, one end of the second return tube 3 is communicated with oil connection 1, the external injector assembly of the other end, oil outlet tube 2 leads to the flame preheat main body.In addition, oil return solenoid valve 60 passes oil returning pipe joint 1 mesopore and is connected with pump cover 20.Cold-start flame-preheating oil feeding device 70 also comprises hydraulic oil-returning valve 4 and transport pipe 6, one end of hydraulic oil-returning valve 4 is communicated with transport pipe 6, the other end is communicated with the first return tube 5, and an end of transport pipe 6 is communicated with oil connection 1, and fuel oil flows into cold-start flame-preheating oil feeding device 70 by transport pipe 6.Hydraulic oil-returning valve 4 is for only to allow liquid to be flowed to the one-way valve of fuel tank by described oil connection 1.The custom-designed return tube parts of the utility model and one-way valve thereof, custom-designed oil return solenoid valve is integrated the fuel oil that the level pressure certain pressure can be provided to the flame preheat main body in conjunction with control system.Both guaranteed the reliability of diesel engine cold start-up, again so that after the cold start-up discharging in diesel oil preheating stage improve, have simultaneously high speed oil return heat radiation assurance function.
Hydraulic leading apparatus is the direct actuator that the dynamic timing of VE type Electrocontrolled high-pressure fuel oil injectionpump shifts to an earlier date, and the power source of its action relies on the fuel pressure of pump chamber fully.As shown in Figure 7, in the utility model specific embodiment, hydraulic pressure sharp time unit 40 comprises piston of timing advance device 4-1, advance device spring 4-4, roller seat pin 4-3, balance staff 4-2, roller 4-5, roller base 4-6, the upper end of roller seat pin 4-3 is inserted into and is arranged in the roller base 4-6 that roller is equipped with in the top, and the lower end vertically is inserted among the balance staff 4-2; Balance staff 4-2 vertically is inserted into piston of timing advance device 4-1 middle part; Piston of timing advance device 4-1 horizontal setting consists of sliding pair with distributing the pump housing, and its two ends form the first space S 1 that communicates with pump housing hyperbaric chamber and the second space S2 that communicates with pump housing low-pressure cavity with the pump housing 10 respectively; Advance device spring 4-4 between piston of timing advance device 4-1 and the pump housing 10 is housed in the second space S2.
As shown in Figure 8, piston of timing advance device 4-1 overall length is 58mm-59mm, and high voltage terminal 61 comprises throttling pore 63 and magnetic cylinder screw 65, and low voltage terminal 62 comprises advance device spring mounting hole 64.As shown in Figure 9, throttling pore 63 diameter ranges are 0.47mm-0.55mm.By changing the throttle orifice flow, in the constant situation of edge condition, changed the pressure proportioning in piston of timing advance device high low pressure chamber, realized hydraulic pressure timing characteristic desired value.
The steel wire diameter scope of advance device spring is 2.98mm-3.02mm in the utility model, and the overall length scope is 33.5mm-34.5mm, and range in stiffness is 69.3N/mm-78.3N/mm, and the spring outer diameter scope is 15.75mm-16.25mm.In the work, increase along with pump chamber pressure, the first space S 1 pressure that communicates with pump housing hyperbaric chamber increases, piston of timing advance device 4-1 begins mobile behind the second space S2 fuel pressure that overcomes advance device spring 4-4 pretightening force and communicate with pump housing low-pressure cavity, and the balance staff 4-2 by the middle part and the roller seat pin 4-3 that inserts in the balance staff make roller base 4-5 turn an angle around axis, and roller base 4-5 is when axis rotates, the roller 4-5 that is installed on the roller base 4-6 rotates simultaneously, thereby changed the relative position of roller and end cam, realized the suitable accent of fuel injection timing.
As seen above-mentioned; After other Parameters of The Parts solidified, the size of pump chamber pressure was the determinant factor of fuel injection timing.And the correct coupling of this pump chamber pressure and advance device spring and related components just can realize required characteristic of fuel delivery curve to a certain extent.When the pressure of pump hyperbaric chamber and body low-pressure cavity balanced each other, it is stable that piston of timing advance device keeps, thereby keep the stable of timing.
Effective combination of the present utility model has improved slow-revving pump chamber pressure, and the slow-speed of revolution timing rotating speed that works so that the effect rotating speed 500 turns in advance, has reduced the timing stroke of high speed stage, so that range reduces more than 2 millimeters.
Shown in Fig. 1-9, when diesel engine starting, high pressure oil pump is namely started working, at once produce pressure owing to be contained in the effect pump chamber internal combustion oil of the oil transfer pump 30 in the VE proportioning pump, pressure oil flows to oil return solenoid valve filler opening as shown in Figure 5, this moment, oil return solenoid valve was in "on" position, rubber tip 16 on the armature component is pressed on the oil mass valve assembly left side, oil-feed mesopore 15 on the oil mass valve assembly is shut, and it is that oil outlet 14 shown in Figure 5 flows out by the vertical aperture on the valve body relative with it by the vertical aperture on the oil mass valve assembly more namely that the fuel oil of inflow only has an outlet.The fuel oil that flows out flows to the flame preheat main body from the oil outlet tube 2 of oil supplying device oil pipe assembly again through cold-start flame-preheating oil feeding device oil pipe assembly, for the flame preheat main body provides corresponding pressure fuel oil.Until the cold-start flame warm-up phase is finished.
After the cold-start flame warm-up phase is finished, when the diesel engine normal working, rotating speed is increased sharply, the pump chamber fuel pressure sharply raises, finish owing to the cold-start flame warm-up phase this moment, oil return solenoid valve 60 is in off-position, rubber tip 16 ineffective power on the armature component, pressure oil is oil outlet 13 shown in Figure 5 and oil outlet 14 by the oil-feed mesopore 15 inflow valve bodies on the oil mass valve assembly and by the vertical aperture on the valve body, flow into cold-start flame-preheating oil feeding device oil pipe assembly, although this moment, oil outlet was not because any change occurs in its connected state, but because this moment, the cold-start flame warm-up phase was finished, flame preheat main body port closing, cold-start flame-preheating oil feeding device oil outlet do not have fuel oil to flow out.When the fuel pressure of rapid rising one-way valve opens during greater than the pressure that is preset at the one-way valve in the cold-start flame-preheating oil feeding device, fuel oil flows into fuel tanks through the first return tube 5, when playing the diesel engine normal working, to the effect of high pressure oil pump heat radiation.
As shown in figure 10, curve 1 is pressure regulation timing advancer timing characteristic; Curve 2 is the intrinsic timing characteristic of former timing mechanism; Curve 3 is the pump chamber pressure of former timing mechanism; Curve 4 is the pump chamber pressure of pressure regulation timing advancer; Be significantly improved low speed segment pressure morning of setting up particularly, rising fast from the pump chamber pressure of the former pressure regulation timing of the pump chamber pressure ratio advancer of curve 4 and curve 3 more visible pressure regulation timing advancers of the present utility model.It is milder than the timing characteristic of former timing mechanism to shift to an earlier date the characteristic tendency from the timing of curve 1 and curve 2 more visible pressure regulation timing advancers, and the timing rotating speed that works in advance greatly shifts to an earlier date.
In above description, a lot of details have been set forth so that fully understand the utility model.But above description only is preferred embodiment of the present utility model, and the utility model can be implemented much to be different from alternate manner described here, so the utility model is not subjected to the restriction of top disclosed implementation.Any skilled personnel are not breaking away from the technical solutions of the utility model scope situation simultaneously, all can utilize method and the technology contents of above-mentioned announcement that technical solutions of the utility model are made many possible changes and modification, or be revised as the equivalent embodiment of equivalent variations.Every content that does not break away from technical solutions of the utility model, any simple modification, equivalent variations and modification according to technical spirit of the present utility model is done above embodiment all still belong to the utility model technology.---whether this sentence is added in the claim.
Claims (12)
1. pressure regulation timing advancer, it is characterized in that, comprise the pump housing, pump cover, oil transfer pump, hydraulic pressure sharp time unit, pressure regulator valve aperture, oil return solenoid valve and cold-start flame-preheating oil feeding device, described oil transfer pump is contained in the described pump housing, the described pump housing becomes sealing to connect with described pump cover, connect through described pressure regulator valve aperture and described oil return solenoid valve, described oil return solenoid valve passes described cold-start flame-preheating oil feeding device oil pipe assembly and is connected with described pump cover.
2. pressure regulation timing advancer as claimed in claim 1 is characterized in that described oil return solenoid valve is two hole oil return solenoid valves, and the above has an oil outlet, and the below has an oil outlet.
3. pressure regulation timing advancer as claimed in claim 2 is characterized in that the oil outlet diameter above the described oil return solenoid valve is 0.8mm, and following oil outlet diameter is 0.5mm.
4. pressure regulation timing advancer as claimed in claim 1, it is characterized in that, described cold-start flame-preheating oil feeding device comprises oil connection, the first return tube, the second return tube, oil outlet tube, the external fuel tank of one end of described the first return tube, one end of described the second return tube is communicated with described oil connection, the external injector assembly of the other end, described oil outlet tube leads to the flame preheat main body.
5. pressure regulation timing advancer as claimed in claim 4 is characterized in that, described oil return solenoid valve passes described oil returning pipe joint mesopore and is connected with described pump cover.
6. pressure regulation timing advancer as claimed in claim 4, it is characterized in that, described cold-start flame-preheating oil feeding device also comprises hydraulic oil-returning valve and transport pipe, one end of described hydraulic oil-returning valve is communicated with described transport pipe, the other end is communicated with described the first return tube, and fuel oil flows into described cold-start flame-preheating oil feeding device by described oil return solenoid valve.
7. pressure regulation timing advancer as claimed in claim 6 is characterized in that, described hydraulic oil-returning valve is for only to allow liquid to be flowed to the one-way valve of fuel tank by described oil connection.
8. pressure regulation timing advancer as claimed in claim 1, it is characterized in that, during described pressure regulation timing advancer work, the pressure fuel oil will flow into described oil return solenoid valve by the described pump housing, described pump cover, flow into described cold-start flame-preheating oil feeding device through described oil return solenoid valve again.
9. pressure regulation timing advancer as claimed in claim 1, it is characterized in that, described hydraulic pressure sharp time unit comprises piston of timing advance device, advance device spring, roller seat pin, balance staff, roller, roller base, the upper end of described roller seat pin is inserted into and is arranged in the described roller base that described roller is equipped with in the top, and the lower end vertically is inserted in the described balance staff; Described balance staff vertically is inserted into described piston of timing advance device middle part; Described piston of timing advance device horizontal setting consists of sliding pair with distributing the pump housing, and its two ends form the first space that communicates with pump housing hyperbaric chamber and the second space that communicates with pump housing low-pressure cavity with the described pump housing respectively; Advance device spring between piston of timing advance device and the pump housing is housed in the described second space.
10. pressure regulation timing advancer as claimed in claim 9, it is characterized in that the steel wire diameter scope of described advance device spring is 2.98mm-3.02mm, the overall length scope is 33.5mm-34.5mm, range in stiffness is 69.3N/mm-78.3N/mm, and the spring outer diameter scope is 15.75mm-16.25mm.
11. pressure regulation timing advancer as claimed in claim 9 is characterized in that described piston of timing advance device overall length is 58mm-59mm, described high voltage terminal comprises throttling pore and the screw of magnetic cylinder is installed that described low voltage terminal comprises the advance device spring mounting hole.
12. pressure regulation timing advancer as claimed in claim 11 is characterized in that described throttling pore diameter range is 0.47mm-0.55mm.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220291460 CN202832919U (en) | 2012-06-20 | 2012-06-20 | Pressure regulation timing advance device |
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| Application Number | Priority Date | Filing Date | Title |
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| CN 201220291460 CN202832919U (en) | 2012-06-20 | 2012-06-20 | Pressure regulation timing advance device |
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| CN202832919U true CN202832919U (en) | 2013-03-27 |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103244328A (en) * | 2012-06-20 | 2013-08-14 | 南京威孚金宁有限公司 | Pressure-regulating timing advancing device |
| CN111288177A (en) * | 2020-04-01 | 2020-06-16 | 上海凌云瑞升燃烧设备有限公司 | Radial fuel flow adjusting device for low-nitrogen combustor |
| CN112081702A (en) * | 2020-10-12 | 2020-12-15 | 河北华北柴油机有限责任公司 | A constant pressure stabilization device for diesel engine preheating system |
-
2012
- 2012-06-20 CN CN 201220291460 patent/CN202832919U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103244328A (en) * | 2012-06-20 | 2013-08-14 | 南京威孚金宁有限公司 | Pressure-regulating timing advancing device |
| CN103244328B (en) * | 2012-06-20 | 2016-06-08 | 南京威孚金宁有限公司 | Pressure regulation timing advancer |
| CN111288177A (en) * | 2020-04-01 | 2020-06-16 | 上海凌云瑞升燃烧设备有限公司 | Radial fuel flow adjusting device for low-nitrogen combustor |
| CN112081702A (en) * | 2020-10-12 | 2020-12-15 | 河北华北柴油机有限责任公司 | A constant pressure stabilization device for diesel engine preheating system |
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