CN103603759A - Phase difference transmission system of engine fuel injection pump - Google Patents
Phase difference transmission system of engine fuel injection pump Download PDFInfo
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- CN103603759A CN103603759A CN201310574938.XA CN201310574938A CN103603759A CN 103603759 A CN103603759 A CN 103603759A CN 201310574938 A CN201310574938 A CN 201310574938A CN 103603759 A CN103603759 A CN 103603759A
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- injection pump
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Abstract
The invention provides a phase difference transmission system of an engine fuel injection pump. The phase difference transmission system used for controlling the fuel injection time of the fuel injection pump comprises a shell, a clutch flange, a spindle adapter, a spindle flange, a planet gear rack, an eccentric wheel and a connecting rod. A planet gear mechanism is disposed on the clutch flange. An eccentric mechanism is disposed between the planet gear mechanism and the spindle adapter. The ratio of the tooth number of an inner tooth gear ring to that of a planet gear is n which equals to the number of the cylinder bodies of the fuel injection pump. By the phase difference transmission system mounted between the power input end and the cam shaft of the fuel injection pump, the fuel injection efficiency of the fuel injection pump can be controlled, fuel combustion rate of the engine is then increased, emission and pollution are reduced, and the output power of the engine is increased.
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 by parts such as Injection Pump, speed regulators the integral body forming.Wherein speed regulator is low-speed running and the restriction to maximum speed that ensures diesel engine, guarantees to keep between emitted dose and rotating speed the parts of certain relation.Injection Pump is the most important parts of diesel engine, is regarded as " heart " parts of diesel engine, once it goes wrong, can make whole diesel engine work not normal.The vital part of Injection Pump is plunger, one end mounting spring of plunger, and plunger the other end contact camshaft, circles when camshaft returns, and plunger will move up and down once in plunger bushing, the basic exercise mode of Here it is injection pump plunger.Plunger and plunger bushing are to process very accurate auxiliary equipment.Plunger has tipper with it one, on plunger bushing, there is aperture to be called suction port, this suction port is diesel oil abrim, when plunger tipper faces toward suction port, diesel oil enters in plunger bushing, when plunger is pushed up to certain altitude by camshaft, plunger tipper and suction port stagger, suction port is closed, diesel oil can not be sucked can not be forced out, when continuing to rise, plunger oppresses diesel oil, diesel oil pressure will back down outlet valve to a certain extent and go out to enter oil nozzle, from oil nozzle, enter combustion chamber of air cylinder again, because the angular velocity of traditional camshaft is constant, therefore cause the outlet valve opening time being 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 and a kind ofly makes Injection Pump oil spout faster, improves rate of combustion, cuts the waste and the phase difference transmission system of the injection pump of engine that pollutes.
(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, is installed with interior toothed ring gear 1 in described housing; 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, planetary pinion 6 with described interior toothed ring gear 1 engagement is installed on described planetary carrier 5 rotationally, the ratio of the number of teeth of the number of teeth of described interior toothed ring gear 1 and described planetary pinion 6 is n, and described ratio n equates 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 be circumferentially distributed on described planetary carrier 5.
Further, the sidewall of described housing offers for cooling filler opening 101 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 connecting successively, eccentric wheel body 72 and bearing assembly department 73, on the end face of described planetary pinion 6, offer attachment hole, described joint 71 is set in the attachment hole of described planetary pinion 6, the axis coaxle of described bearing assembly department 73 and described planetary pinion 6, and the axis disalignment of the axis of described eccentric wheel body 72 and described planetary pinion 6, described connecting rod 8 is set on described eccentric wheel body 72 rotationally by sliding bearing, described bearing assembly department 73 is arranged on described planetary carrier 5 rotationally by sliding bearing.
Further, the cross section of described joint 71 is ellipse or regular polygon.
Further, described housing comprises by bolted left end cap 91 and right end cap 92, between described left end cap 91 and right end cap 92, is tightly connected.
Further, the ratio n six of the number of teeth of the number of teeth of described interior toothed ring gear 1 and described planetary pinion 6.
(3) beneficial effect
The phase difference transmission system of injection pump of engine of the present invention, by eccentric, realize the variation of angular acceleration, its whole period of rotation inconvenience, at planetary pinion, when circling, a cam on camshaft produces the angular acceleration of a variation, has reduced injection time, improved oil spout efficiency, and then improved rate of combustion, and reduced disposal of pollutants, reduced the pollution to air, the number of teeth of interior toothed ring gear equates with the number of the cylinder body of Injection Pump with the ratio of the planetary number of teeth, equate with the cylinder body number of motor, therefore, planetary pinion public affairs on gear ring circle, the number of acceleration forming and the number of the cylinder body of Injection Pump equate, be that camshaft rotates a circle, the number of the acceleration of its formation equates 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 oily rate of combustion, reduce discharge and pollute, improved 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, thereby 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 for applying the Motion curves of the plunger after 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 by seal ring, realize and being tightly connected between left end cap 91 and right end cap 92, sidewall at housing offers for cooling filler opening 101 and oil outlet 102, is installed with interior toothed ring gear 1 in this housing; Clutch flange 2 for power input is arranged on one end of housing rotationally by bearing; Spindle adapter 3 for power output is arranged on the other end of housing rotationally by bearing, and coaxially arranges 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 pinion 6 with interior toothed ring gear 1 engagement is installed rotationally on planetary carrier 5, this planetary pinion 6 is at least three and be circumferentially 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 the number of teeth of interior toothed ring gear 1 and planetary pinion 6 is n, and this ratio n equates with the cylinder body number of Injection Pump; Such as, the cylinder body number of Injection Pump is 3, this ratio n is also 3, 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, this ratio n is also 6, and the ratio of the interior 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 rotationally by sliding bearing; In order to improve output stability, at the two ends of planetary pinion 6, be equipped with eccentric wheel 7, connecting rod 8 is set on eccentric wheel 7 rotationally by sliding bearing; In the present embodiment, this eccentric wheel 7 comprises joint 71, eccentric wheel body 72 and the bearing assembly department 73 connecting successively, on the end face of planetary pinion 6, offer attachment hole, joint 71 is set in the attachment hole of this planetary pinion 6, the axis coaxle of bearing assembly department 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 rotationally by sliding bearing, and bearing assembly department 73 is arranged on planetary carrier 5 rotationally by sliding bearing; For the ease of installing and avoiding producing relative rotation, the cross section of this joint 71 is non-circular, preferably ellipse or regular polygon.
During work, power is from clutch flange 2 end inputs, drive the planetary carrier 5 of its end to rotate, and then drive planetary pinion 6 uniform rotation on this planetary carrier 5, the eccentric wheel 7 that is positioned at these planetary pinion 6 ends 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, in rotation process, there is certain angular acceleration in spindle flange, planetary pinion 6 is from circling, spindle flange completes an angular acceleration cycle, a cam on the camshaft being 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 equates with the number of the cylinder body of Injection Pump, and each cam on the camshaft being 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 n angular acceleration of ratio, each cam of controlling on the fuel injection camshaft that is positioned at output terminal all completes an angular acceleration rotation, and then the ejection cycle of the plunger on control cam shortens, shortened the opening time of outlet valve, but fuel injection quantity is inconvenient, improved fuel injection rate, thereby the rate of combustion of motor is improved, made oil firing more complete, reduce blowdown, improved 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; Such as ratio n is 3 o'clock, the cylinder body number of Injection Pump is 3 o'clock, and the curve of collection is as follows;
As shown in Figure 7, the rotation angular acceleration curve of a week that this curve is output terminal of the present invention, as seen from the figure, within the rotation time of one week, there are three angular acceleration change in main shaft output, and its period of change equates;
Fig. 8 is the velocity curve that ejects of one of them plunger of controlling of the camshaft of former Injection Pump;
Fig. 9 is one of them plunger of increasing the camshaft of the Injection Pump after the phase difference transmission system of injection pump of engine of the present invention at the input end of camshaft and controlling ejects velocity curve, by this figure, can be found out, the speed of plunger when ejecting is compared traditional speed and is wanted fast, the opening speed that is outlet valve accelerates, the in the situation that of fuel injection quantity inconvenience, oil spout speed accelerates, can make the thinner of oil burning jet, can make it burn more fully, and then improved rate of combustion, reduce discharge, also improved the output power of motor simultaneously.
The phase difference transmission system of injection pump of engine of the present invention, by eccentric, realize the variation of angular acceleration, its whole period of rotation inconvenience, at planetary pinion, when circling, a cam on camshaft produces the angular acceleration of a variation, has reduced injection time, improved oil spout efficiency, and then improved rate of combustion, and reduced disposal of pollutants, reduced the pollution to air, the number of teeth of interior toothed ring gear equates with the number of the cylinder body of Injection Pump with the ratio of the planetary number of teeth, equate with the cylinder body number of motor, therefore, planetary pinion public affairs on gear ring circle, the number of acceleration forming and the number of the cylinder body of Injection Pump equate, be that camshaft rotates a circle, the number of the acceleration of its formation equates 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 oily rate of combustion, reduce discharge and pollute, improved 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, thereby 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, do not departing under the prerequisite of 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, is installed with interior toothed ring gear in described housing;
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, planetary pinion with described interior toothed ring gear engagement is installed on described planetary carrier rotationally, 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 equates 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 be circumferentially 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 for cooling filler opening and oil outlet.
4. the phase difference transmission system of injection pump of engine as claimed in claim 1, is characterized in that: described planetary carrier is two and be arranged in parallel, and 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 connecting successively, eccentric wheel body and bearing assembly department, on described planetary end face, offer attachment hole, described joint is set in described planetary attachment hole, described bearing assembly department 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 rotationally by sliding bearing, described bearing assembly department 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 ellipse 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, between described left end cap and right end cap, is tightly connected.
9. the phase difference transmission system of the injection pump of engine as described in claim 1 to 8 any one, 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 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103603759A true CN103603759A (en) | 2014-02-26 |
| CN103603759B CN103603759B (en) | 2015-10-14 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| 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) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105909437A (en) * | 2016-05-06 | 2016-08-31 | 潍柴动力扬州柴油机有限责任公司 | Fuel pump transmission device and fuel injection system comprising same |
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 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105909437A (en) * | 2016-05-06 | 2016-08-31 | 潍柴动力扬州柴油机有限责任公司 | Fuel pump transmission device and fuel injection system comprising same |
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103603759B (en) | 2015-10-14 |
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Granted publication date: 20151014 Termination date: 20181115 |
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