CN103603759B - The phase difference transmission system of injection pump of engine - Google Patents
The phase difference transmission system of injection pump of engine Download PDFInfo
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- CN103603759B CN103603759B CN201310574938.XA CN201310574938A CN103603759B CN 103603759 B CN103603759 B CN 103603759B CN 201310574938 A CN201310574938 A CN 201310574938A CN 103603759 B CN103603759 B CN 103603759B
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- injection pump
- planetary
- engine
- phase difference
- transmission system
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Abstract
The invention provides a kind of phase difference transmission system of injection pump of engine, for controlling the injection time of Injection Pump, it comprises housing, clutch flange, spindle adapter, spindle flange, planetary carrier, eccentric wheel and connecting rod, clutch flange is provided with planetary gears, eccentric stiffener is provided with between this planetary gears and spindle adapter, simultaneously, the number of teeth of toothed ring gear and the ratio of the planetary number of teeth are n, and ratio n is equal with the cylinder body number of Injection Pump.The phase difference transmission system of injection pump of engine of the present invention, be arranged on the oil spout efficiency that can control Injection Pump between power intake and fuel injection camshaft, and then improving motor to the rate of combustion of oil, emissions reduction and pollution, improve the output power of motor simultaneously.
Description
Technical field
The present invention relates to a kind of injection pump of engine, particularly a kind of phase difference transmission system of injection pump of engine.
Background technique
Injection Pump is an important component part on diesel engine of vehicle.Injection pump assembly is normally installed together the entirety formed by the parts such as Injection Pump, speed regulator.Wherein speed regulator ensures the low-speed running of diesel engine and the restriction to maximum speed, guarantees the parts keeping certain relation between emitted dose and rotating speed.Injection Pump is then the most important parts of diesel engine, is regarded as " heart " parts of diesel engine, and it can make whole diesel engine work not normal once go wrong.The vital part of Injection Pump is plunger, one end mounting spring of plunger, and plunger the other end contact camshaft, circle when camshaft returns, plunger will move up and down once in plunger bushing, the basic exercise mode of Here it is injection pump plunger.Very accurate auxiliary equipment processed by plunger and plunger bushing.Plunger has one tipper with it, plunger bushing there is aperture be called suction port, this suction port diesel oil abrim, when plunger tipper is facing to suction port, diesel oil enters in plunger bushing, plunger by camshaft top to certain altitude time, plunger tipper and suction port stagger, suction port is closed, diesel oil can not be sucked can not be forced out, compressing diesel oil when plunger continues to rise, diesel pressure will back down outlet valve to a certain extent and go out to enter oil nozzle, combustion chamber of air cylinder is entered again from oil nozzle, angular velocity due to traditional camshaft is constant, therefore cause the outlet valve opening time backed down by plunger excessively slow, cause diesel combustion incomplete, form waste and pollute.
Summary of the invention
(1) technical problem that will solve
The technical problem to be solved in the present invention is to provide one makes Injection Pump oil spout faster, improves rate of combustion, the phase difference transmission system of injection pump of engine cutting the waste and pollute.
(2) technological scheme
For solving the problems of the technologies described above, the invention provides a kind of phase difference transmission system of injection pump of engine, for controlling the injection time of Injection Pump, comprising: housing, described housing internal fixtion is provided with interior toothed ring gear 1; Clutch flange 2, for power input, it is arranged on one end of described housing rotationally; Spindle adapter 3, for Power output, it is arranged on the other end of described housing rotationally, and coaxially arranges with described clutch flange 2; Spindle flange 4, described spindle flange 4 is positioned at described housing, and is fixedly connected on the end of described spindle adapter 3; Planetary carrier 5, described planetary carrier 5 is positioned at described housing and is fixedly connected on the end of described clutch flange 2, described planetary carrier 5 is provided with rotationally the planetary pinion 6 engaged with described interior toothed ring gear 1, the ratio of the number of teeth of described interior toothed ring gear 1 and the number of teeth of described planetary pinion 6 is n, and described ratio n is equal with the cylinder body number of described Injection Pump; Eccentric wheel 7, described eccentric wheel 7 is fixedly connected on the end of described planetary pinion 6, and the axis disalignment of the axis of described eccentric wheel 7 and described planetary pinion 6; Connecting rod 8, one end of described connecting rod 8 is set on described eccentric wheel 7 rotationally, and the other end of described connecting rod 8 is hinged on the edge of described spindle flange 4 rotationally.
Further, described planetary pinion 6 is at least three and circumference is distributed on described planetary carrier 5.
Further, the sidewall of described housing offers filler opening 101 for cooling and oil outlet 102.
Further, described planetary carrier 5 is two and be arranged in parallel, and described planetary pinion 6 is arranged between described two planetary carriers 5 rotationally by sliding bearing.
Further, the two ends of described planetary pinion 6 are equipped with described eccentric wheel 7, and described connecting rod 8 is set on described eccentric wheel 7 rotationally by sliding bearing.
Further, described eccentric wheel 7 comprises the joint 71 connected successively, eccentric wheel body 72 and axle bearing mount portion 73, the end face of described planetary pinion 6 offers attachment hole, described joint 71 is set in the attachment hole of described planetary pinion 6, the axis coaxle of described axle bearing mount portion 73 and described planetary pinion 6, and the axis of described eccentric wheel body 72 and the axis disalignment of described planetary pinion 6, described connecting rod 8 is set on described eccentric wheel body 72 by sliding bearing rotationally, described axle bearing mount portion 73 is arranged on described planetary carrier 5 rotationally by sliding bearing.
Further, the cross section of described joint 71 is oval or regular polygon.
Further, described housing comprises by bolted left end cap 91 and right end cap 92, is tightly connected between described left end cap 91 and right end cap 92.
Further, the ratio n six of the number of teeth of described interior toothed ring gear 1 and the number of teeth of described planetary pinion 6.
(3) beneficial effect
The phase difference transmission system of injection pump of engine of the present invention, the change of angular acceleration is realized by eccentric, its whole period of rotation inconvenience, at planetary pinion in time circling, a cam on camshaft produces the angular acceleration of a change, decreases injection time, improve oil spout efficiency, and then improve rate of combustion, reduce disposal of pollutants, decrease the pollution to air, the number of teeth of interior toothed ring gear is equal with the number of the cylinder body of Injection Pump with the ratio of the planetary number of teeth, namely equal with the cylinder body number of motor, therefore, planetary pinion public affairs on gear ring circle, the number of acceleration formed is equal with the number of the cylinder body of Injection Pump, namely camshaft rotates a circle, the number of its acceleration formed is equal with the cam number on camshaft, the phase difference transmission system of injection pump of engine of the present invention, be arranged on the oil spout efficiency that can control Injection Pump between power intake and fuel injection camshaft, and then improve motor to the rate of combustion of oil, emissions reduction and pollution, improve the output power of motor simultaneously, the phase difference transmission system of injection pump of engine of the present invention can be transformed on existing injection pump of engine, thus improve rate of combustion and the output power of motor.
Accompanying drawing explanation
Fig. 1 is the explosive view of the phase difference transmission system of injection pump of engine of the present invention;
Fig. 2 is the internal structure schematic diagram of the phase difference transmission system of injection pump of engine of the present invention;
Fig. 3 is the transverse sectional view of the phase difference transmission system of injection pump of engine of the present invention;
Fig. 4 is the longitudinal sectional view of the phase difference transmission system of injection pump of engine of the present invention;
Fig. 5 is the eccentric structural representation of the phase difference transmission system of injection pump of engine of the present invention;
Fig. 6 is the application structure figure of the phase difference transmission system of injection pump of engine of the present invention;
Fig. 7 is the rotation curve of output of spindle adapter in the phase difference transmission system of injection pump of engine of the present invention;
Fig. 8 is the Motion curves of former injection pump plunger;
Fig. 9 is the Motion curves of the plunger after application the present invention.
Embodiment
Consult Fig. 1 ~ Fig. 9, the invention provides a kind of phase difference transmission system of injection pump of engine, for controlling the injection time of Injection Pump, it comprises: housing, clutch flange 2, spindle adapter 3, spindle flange 4, planetary carrier 5, eccentric wheel 7 and connecting rod 8; Housing comprises by bolted left end cap 91 and right end cap 92, and realize being tightly connected by seal ring between left end cap 91 and right end cap 92, offering filler opening 101 for cooling and oil outlet 102 at the sidewall of housing, at this housing internal fixtion, interior toothed ring gear 1 being installed; Clutch flange 2 for power input to be arranged on one end of housing rotationally by bearing; Be arranged on the other end of housing for the spindle adapter 3 of Power output by bearing rotationally, and coaxially arrange with clutch flange 2; Spindle flange 4 is positioned at housing, and is fixedly connected on the end of spindle adapter 3; Planetary carrier 5 is also positioned at housing and is fixedly connected on the end of clutch flange 2, planetary carrier 5 is provided with planetary pinion 6 rotationally that engage with interior toothed ring gear 1, this planetary pinion 6 is at least three and circumference is distributed on planetary carrier 5, preferably, this planetary pinion 6 is three, now, structural strength is the highest, meanwhile, the ratio of the number of teeth of interior toothed ring gear 1 and the number of teeth of planetary pinion 6 is n, and this ratio n is equal with the cylinder body number of Injection Pump; Such as, the cylinder body number of Injection Pump is 3, then this ratio n is also 3, namely in, the ratio of the number of teeth of toothed ring gear 1 and the number of teeth of planetary pinion 6 is 3, and and for example, the cylinder body number of Injection Pump is 6, then this ratio n is also 6, and namely, the ratio of the number of teeth of toothed ring gear 1 and the number of teeth of planetary pinion 6 is 6; Eccentric wheel 7 is fixedly connected with (being rigidly connected) in the end of planetary pinion 6, and the axis disalignment of the axis of this eccentric wheel 7 and planetary pinion 6; One end of connecting rod 8 is set on eccentric wheel 7 rotationally, and the other end of connecting rod 8 is hinged on the edge of spindle flange 4 rotationally; In order to improve the stability of planetary operation, planetary carrier 5 is two and be arranged in parallel, and planetary pinion 6 is arranged between this two planetary carrier 5 by sliding bearing rotationally; In order to improve output stability, be equipped with eccentric wheel 7 at the two ends of planetary pinion 6, connecting rod 8 is set on eccentric wheel 7 by sliding bearing rotationally; In the present embodiment, this eccentric wheel 7 comprises the joint 71, eccentric wheel body 72 and the axle bearing mount portion 73 that connect successively, the end face of planetary pinion 6 offers attachment hole, joint 71 is set in the attachment hole of this planetary pinion 6, the axis coaxle of axle bearing mount portion 73 and planetary pinion 6, and the axis disalignment of the axis of eccentric wheel body 72 and planetary pinion 6, connecting rod 8 is set on eccentric wheel body 72 by sliding bearing rotationally, and axle bearing mount portion 73 is arranged on planetary carrier 5 by sliding bearing rotationally; For the ease of installing and avoiding producing relative rotation, the cross section of this joint 71 is non-circular, preferably oval or regular polygon.
During work, power inputs from clutch flange 2 end, the planetary carrier 5 of its end is driven to rotate, and then drive planetary pinion 6 uniform rotation on this planetary carrier 5, the eccentric wheel 7 being positioned at this planetary pinion 6 end rotates prejudicially, by connecting rod, this rotation is passed to spindle flange 4, because spindle flange is connected on eccentric wheel by connecting rod, therefore, certain angular acceleration is there is in spindle flange in rotation process, planetary pinion 6 is from circling, spindle flange completes an angular acceleration cycle, namely a cam on the camshaft be connected with spindle adapter completes an angle accelerating period, planetary pinion 6 public affairs circle, spindle flange completes ratio n angular acceleration cycle, this ratio n is the ratio of the number of teeth of interior toothed ring gear 1 and the number of teeth of planetary pinion 6, it is equal with the number of the cylinder body of Injection Pump, and each cam on the camshaft be namely connected with spindle adapter all completes an angle accelerating period, input end of the present invention at the uniform velocity rotates a circle, output terminal also rotates one week, but output terminal is in this week, there is ratio n angular acceleration, namely control each cam be positioned on the fuel injection camshaft of output terminal and all complete an angular acceleration rotation, and then the ejection cycle of plunger on control cam shortens, shorten the opening time of outlet valve, but fuel injection quantity is inconvenient, namely improve fuel injection rate, thus the rate of combustion of motor is improved, make oil firing more complete, decrease blowdown, improve fuel utilization ratio and engine power simultaneously.
The phase difference transmission system of following injection pump of engine of the present invention should be used as brief description; When such as ratio n is 3, when namely the cylinder body number of Injection Pump is 3, the curve of collection is as follows;
As shown in Figure 7, this curve is the rotation angular acceleration curve of a week of output terminal of the present invention, and as seen from the figure, within the rotation time of one week, main shaft exports appearance three angular acceleration change, and its period of change is equal;
Fig. 8 be former Injection Pump camshaft control one of them plunger eject velocity curve;
Fig. 9 be one of them plunger of controlling of the camshaft of Injection Pump after the input end of camshaft increases the phase difference transmission system of injection pump of engine of the present invention eject velocity curve, as can be seen from this figure, the speed of plunger when ejecting is compared traditional speed and is wanted fast, namely the opening speed of outlet valve accelerates, when fuel injection quantity inconvenience, injection velocity accelerates, the thinner of oil burning jet can be made, it can be made to burn more fully, and then improve rate of combustion, reduce discharge, also improve the output power of motor simultaneously.
The phase difference transmission system of injection pump of engine of the present invention, the change of angular acceleration is realized by eccentric, its whole period of rotation inconvenience, at planetary pinion in time circling, a cam on camshaft produces the angular acceleration of a change, decreases injection time, improve oil spout efficiency, and then improve rate of combustion, reduce disposal of pollutants, decrease the pollution to air, the number of teeth of interior toothed ring gear is equal with the number of the cylinder body of Injection Pump with the ratio of the planetary number of teeth, namely equal with the cylinder body number of motor, therefore, planetary pinion public affairs on gear ring circle, the number of acceleration formed is equal with the number of the cylinder body of Injection Pump, namely camshaft rotates a circle, the number of its acceleration formed is equal with the cam number on camshaft, the phase difference transmission system of injection pump of engine of the present invention, be arranged on the oil spout efficiency that can control Injection Pump between power intake and fuel injection camshaft, and then improve motor to the rate of combustion of oil, emissions reduction and pollution, improve the output power of motor simultaneously, the phase difference transmission system of injection pump of engine of the present invention can be transformed on existing injection pump of engine, thus improve rate of combustion and the output power of motor.
The above is only the preferred embodiment of the present invention; it should be pointed out that for those skilled in the art, under the prerequisite not departing from the technology of the present invention principle; can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.
Claims (9)
1. a phase difference transmission system for injection pump of engine, for controlling the injection time of Injection Pump, is characterized in that, comprising:
Housing, described housing internal fixtion is provided with interior toothed ring gear;
Clutch flange, for power input, it is arranged on one end of described housing rotationally;
Spindle adapter, for Power output, it is arranged on the other end of described housing rotationally, and coaxially arranges with described clutch flange;
Spindle flange, described spindle flange is positioned at described housing, and is fixedly connected on the end of described spindle adapter;
Planetary carrier, described planetary carrier is positioned at described housing and is fixedly connected on the end of described clutch flange, described planetary carrier is provided with rotationally the planetary pinion engaged with described interior toothed ring gear, the number of teeth of described interior toothed ring gear and the ratio of the described planetary number of teeth are n, and described ratio n is equal with the cylinder body number of described Injection Pump;
Eccentric wheel, described eccentric wheel is fixedly connected on described planetary end, and described eccentric axis and described planetary axis disalignment;
Connecting rod, one end of described connecting rod is set on described eccentric wheel rotationally, and the other end of described connecting rod is hinged on the edge of described spindle flange rotationally.
2. the phase difference transmission system of injection pump of engine as claimed in claim 1, is characterized in that: described planetary pinion is at least three and circumference is distributed on described planetary carrier.
3. the phase difference transmission system of injection pump of engine as claimed in claim 1, is characterized in that: the sidewall of described housing offers filler opening for cooling and oil outlet.
4. the phase difference transmission system of injection pump of engine as claimed in claim 1, it is characterized in that: described planetary carrier is two and be arranged in parallel, described planetary pinion is arranged between described two planetary carriers rotationally by sliding bearing.
5. the phase difference transmission system of injection pump of engine as claimed in claim 1, is characterized in that: described planetary two ends are equipped with described eccentric wheel, and described connecting rod is set on described eccentric wheel rotationally by sliding bearing.
6. the phase difference transmission system of injection pump of engine as claimed in claim 5, it is characterized in that: described eccentric wheel comprises the joint connected successively, eccentric wheel body and axle bearing mount portion, described planetary end face offers attachment hole, described joint is set in described planetary attachment hole, described axle bearing mount portion and described planetary axis coaxle, and the axis of described eccentric wheel body and described planetary axis disalignment, described connecting rod is set on described eccentric wheel body by sliding bearing rotationally, described axle bearing mount portion is arranged on described planetary carrier rotationally by sliding bearing.
7. the phase difference transmission system of injection pump of engine as claimed in claim 6, is characterized in that: the cross section of described joint is oval or regular polygon.
8. the phase difference transmission system of injection pump of engine as claimed in claim 1, is characterized in that: described housing comprises by bolted left end cap and right end cap, is tightly connected between described left end cap and right end cap.
9. the phase difference transmission system of the injection pump of engine as described in any one of claim 1 to 8, is characterized in that: the number of teeth of described interior toothed ring gear and the ratio of the described planetary number of teeth are six.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310574938.XA CN103603759B (en) | 2013-11-15 | 2013-11-15 | The phase difference transmission system of injection pump of engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310574938.XA CN103603759B (en) | 2013-11-15 | 2013-11-15 | The phase difference transmission system of injection pump of engine |
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| Publication Number | Publication Date |
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| CN103603759A CN103603759A (en) | 2014-02-26 |
| CN103603759B true CN103603759B (en) | 2015-10-14 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201310574938.XA Expired - Fee Related CN103603759B (en) | 2013-11-15 | 2013-11-15 | The phase difference transmission system of injection pump of engine |
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| CN (1) | CN103603759B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105909437B (en) * | 2016-05-06 | 2018-11-23 | 潍柴动力扬州柴油机有限责任公司 | A kind of fuel pump transmission device and the fuel injection system equipped with the device |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4389998A (en) * | 1979-10-24 | 1983-06-28 | Diesel Kiki Co., Ltd. | Distribution type fuel injection pump |
| US4401076A (en) * | 1981-04-20 | 1983-08-30 | Hitachi, Ltd. | Fuel injection control system for electromagnetic valve-controlled fuel injection pump of diesel engine |
| US4497303A (en) * | 1981-12-11 | 1985-02-05 | Nippondenso Co., Ltd. | Fuel injection timing device for internal combustion engines |
| CN203532124U (en) * | 2013-11-15 | 2014-04-09 | 宁波富莱茵汽车部件有限公司 | Phase difference drive system of engine fuel injection pump |
-
2013
- 2013-11-15 CN CN201310574938.XA patent/CN103603759B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4389998A (en) * | 1979-10-24 | 1983-06-28 | Diesel Kiki Co., Ltd. | Distribution type fuel injection pump |
| US4401076A (en) * | 1981-04-20 | 1983-08-30 | Hitachi, Ltd. | Fuel injection control system for electromagnetic valve-controlled fuel injection pump of diesel engine |
| US4497303A (en) * | 1981-12-11 | 1985-02-05 | Nippondenso Co., Ltd. | Fuel injection timing device for internal combustion engines |
| CN203532124U (en) * | 2013-11-15 | 2014-04-09 | 宁波富莱茵汽车部件有限公司 | Phase difference drive system of engine fuel injection pump |
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| CN103603759A (en) | 2014-02-26 |
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