CN105065165A - Plunger and plunger coupling piece of diesel engine fuel injection pump - Google Patents
Plunger and plunger coupling piece of diesel engine fuel injection pump Download PDFInfo
- Publication number
- CN105065165A CN105065165A CN201510491925.5A CN201510491925A CN105065165A CN 105065165 A CN105065165 A CN 105065165A CN 201510491925 A CN201510491925 A CN 201510491925A CN 105065165 A CN105065165 A CN 105065165A
- Authority
- CN
- China
- Prior art keywords
- plunger
- injection pump
- sealing surface
- groove
- cavity
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Abstract
A plunger of a diesel engine fuel injection pump comprises a drive end (11), an oil pressing end (13) and a sealing face (12). The sealing face is provided with a plurality of grooves (22) and cavities (24), wherein the cavities (24) are evenly distributed in the positions where grooves are not formed. The sum of the areas formed by the junctions of the grooves and the sealing face is 5%-35% of the theoretical circumferential superficial area of the sealing face. The depth of the grooves is gradually increased from the position close to the oil pressing end to the position close to the drive end. The sum of the areas formed by the junctions of the cavities and the sealing face is 2%-30% of the theoretical circumferential superficial area of the sealing face. The invention further provides a plunger coupling piece of the fuel injection pump. Lubrication between the plunger and a plunger sleeve is improved, and the phenomenon of meshing is reduced. The sealing performance under the conditions of high temperature and high pressure is improved, and fuel leakage is reduced.
Description
Technical field
The present invention relates to the Injection Pump of diesel engine, particularly the plunger of diesel injection pump and plunger coupled parts.
Background technique
Injection Pump is the most important parts of diesel engine, is regarded as " heart " parts of diesel engine.In numerous component of diesel injection pump, plunger and plunger bushing are a pair most important precision pairs in Injection Pump, and mainly play and control fuel injection quantity and the effect producing high jet pressure, its working environment is extremely severe.
Diesel engines at present injection pressure is generally up to more than 180MPa, at plunger force feed process mesohigh fuel oil very easily by the clearance leakage between plunger and plunger bushing in low tension loop, in order to realize superelevation jet pressure, pressure in Injection Pump pumping cavity promotes gradually, and the quantity of fuel leakage caused also sharply increases.
When high pressure fuel leak, pressure is converted into heat energy thereupon, and plunger and plunger bushing structural member are because being heated to high temperature, and fuel oil temperature is raised once again, causes fuel-viscosity variation to decline, its leakage rate increases further, forms vicious circle thus.In addition, the fuel oil deterioration that high temperature causes and the kinematical viscosity decline of fuel oil can cause lubrication effect to be deteriorated, and make the insufficient lubrication between plunger and plunger bushing, both easily produce and kill phenomenon, greatly reduce the working life of Injection Pump.
Summary of the invention
The object of the invention is the lubrication improved between the plunger of diesel injection pump and plunger bushing, what minimizing plunger and plunger bushing produced kills phenomenon, and the sealability between the plunger improved under high-temperature and high-pressure conditions and plunger bushing, reduce the leakage of fuel oil.
For this reason, the invention provides a kind of plunger of diesel injection pump, it comprises a drive end, a force feed end, with a sealing surface, sealing surface is offered many grooves, the angle of the axis of groove and plunger is 30 ° to 70 °, the area sum that each groove and sealing surface intersection are formed be the circumferential theoretical surface of sealing surface long-pending 5% to 35%, the degree of depth of each groove increases near drive end place from it gradually near force feed end, sealing surface is not offered groove and is then evenly equipped with cavity, the area that cavity and sealing surface intersection are formed be the circumferential theoretical surface of sealing surface long-pending 2% to 30%.
In a kind of exemplary embodiment of the plunger of diesel injection pump, a plurality of grooves are parallel to each other.
In a kind of exemplary embodiment of the plunger of diesel injection pump, the Elongation of each groove is 2 to 6.
In the another kind of exemplary embodiment of the plunger of diesel injection pump, the bottom land of each groove and the tangential angle of sealing surface intersection are 10 ° to 45 °
In another exemplary embodiment of the plunger of diesel injection pump, the width of each groove is 10 μm to 30 μm,
The diameter of each cavity is 10 μm to 50 μm.
Present invention also offers a kind of plunger coupled parts of diesel injection pump, it comprises the plunger bushing of a plunger of the present invention and a sheathed plunger, there is between plunger bushing and plunger a radial clearance, wherein the maximum depth of cavity is 0.4 to 5.3 with the ratio of radial clearance, and the maximum cup depth of groove is 0.5 to 6.7 with the ratio of radial clearance.
Adopt plunger of the present invention and plunger coupled parts, in force feed stroke, the fuel oil in groove can be extruded, between plunger and plunger bushing, produce high pressure, form a high-pressure sealing chamber, the High-pressure phase equilibria produced with force feed, thus realize the effect of sealing; Simultaneously when plunger moves in plunger bushing, cavity contributes between plunger and plunger bushing, form the hydrodynamic lubrication oil film with certain thickness and bearing capacity, makes plunger and plunger bushing form contactless slip, greatly improves lubricating condition.The composite structure of cavity of the present invention and varying depth groove, improves lubrication and the sealing of plunger coupled parts simultaneously.
Accompanying drawing explanation
The following drawings only schematically illustrates the present invention and explains, not delimit the scope of the invention.
Fig. 1 is the schematic perspective view of the plunger for illustration of Injection Pump.
Fig. 2 is the plunger close-up schematic view in Fig. 1 shown in II.
Fig. 3 is the schematic diagram of section shown in III-III line in Fig. 1.
Fig. 4 is the cross-sectional schematic of the plunger coupled parts for illustration of Injection Pump.
Fig. 5 is the plunger coupled parts part section enlarged diagram in Fig. 4 shown in V.
Label declaration
10 plungers
11 drive ends
12 sealing surfaces
13 force feed ends
22 grooves
24 cavitys
30 plunger bushings.
Embodiment
In order to the technical characteristics to invention, object and effect have understanding clearly, now contrast accompanying drawing and the specific embodiment of the present invention is described, label identical in the various figures represents same or analogous part.Accompanying drawing, only for illustration of the present invention, does not represent practical structures of the present invention and actual proportions.
Fig. 1 is the schematic perspective view of the plunger for illustration of Injection Pump, as shown in Figure 1, the plunger 10 of diesel injection pump comprises a drive end 11, force feed end 13 and a sealing surface 12, sealing surface 12 is offered many grooves 22, the position not offering groove 22 at sealing surface 12 is then evenly equipped with cavity 24.In mode of execution shown in the figure, a plurality of grooves 22 are parallel to each other, and more easily process, and certainly according to the difference that design needs, a plurality of grooves also can be not parallel to each other mutually.
Groove 22 on the sealing surface 12 of plunger is can be 30 ° to 70 ° with the angle β of the axis of plunger.Fig. 2 is the plunger close-up schematic view in Fig. 1 shown in II, as shown in Figure 2, the width W of groove can be 10 μm to 30 μm, the length L of groove and the ratio of width W can be 2 to 6, the area sum that each groove 22 and sealing surface 12 intersection are formed can be the circumferential theoretical surface of sealing surface 12 long-pending 5% to 35%, the area sum that each cavity 24 and sealing surface 12 intersection are formed be the circumferential theoretical surface of sealing surface 12 amass 2% to 30%.The circumferential theoretical surface of sealing surface 12 is long-pending refers to that peripheral surface when being made up of smooth surface is completely amassed if sealing surface 12 does not have groove and cavity.
In a kind of exemplary embodiment, the diameter of plunger is 7.5mm, the sealing surface 12 of plunger offers five grooves 22, the angle β of they and plunger axis is 45 °, the width W of each groove is 20 μm, the length L of groove is 4 with the ratio of width W, the area that groove 22 and sealing surface 12 intersection are formed be the circumferential theoretical surface of sealing surface 12 amass 22%, the diameter of each cavity 24 for being 30 μm, the area sum that all cavitys and sealing surface 12 intersection are formed be the circumferential theoretical surface of sealing surface 12 long-pending 25%.
Fig. 3 is the schematic diagram along section shown in III-III line in Fig. 1.As shown in Figure 3, on the sealing surface 12 of the plunger of Injection Pump, the degree of depth of groove 22 is changes, namely along its near force feed end 13 place to close drive end 11, the degree of depth of groove 22 on plunger radial direction increases gradually.As namely near force feed end 13 place, the degree of depth of groove 22 is 0, and near drive end 11 place, the degree of depth of groove 22 is h3.Such as, in a kind of exemplary embodiment, the degree of depth h3 of groove 22 is 6 μm, and the bottom land 23 of groove 22 is 30 ° with the tangential angle theta of sealing surface 12 intersection.In fuel feed pump plunger force feed process, this varying depth structure of groove 22, can make the fuel oil pressing to bottom land 22 be squeezed and produce good high pressure seal result, thus effectively reduce quantity of fuel leakage.
In other exemplary embodiment of the plunger of diesel injection pump, groove 22 can at the range content of 30 ° to 70 ° with the angle β of plunger axis, the width W of groove 22 can in the scope of 10 μm to 30 μm, its Elongation can in the scope of 2 to 6, the bottom land 23 of groove 22 and the tangential angle theta of sealing surface 12 intersection can in the scopes of 10 ° to 45 °, the area that institute fluted 22 and sealing surface 12 intersection are formed be the circumferential theoretical surface of sealing surface 12 amass 5% to 35%; The diameter of each cavity 24 is 10 μm to 50 μm, the area that all cavity 24 and sealing surface 12 intersection are formed be the circumferential theoretical surface of sealing surface 12 amass 2% to 30%.
Fig. 4 is the cross-sectional schematic of the plunger coupled parts for illustration of Injection Pump, and the plunger coupled parts of diesel injection pump comprises plunger 10 and plunger bushing 30 as shown in the figure.The structure of plunger 10 as shown in Figure 1, does not repeat them here, the sheathed plunger 10 of plunger bushing 30.Fig. 5 is the plunger coupled parts close-up schematic view in Fig. 4 shown in V, and as shown in Figure 5, have a radial clearance h2 between it and plunger 10, the maximum depth h1 of cavity 24 is 0.4 to 5.3 with the ratio of radial clearance h2.Such as in the schematic mode of execution of one, the maximum depth h1 of cavity 24 is 3 with the ratio of radial clearance h2.Each miniature cavity forms the hydrodynamic pressure with bearing capacity, and all cavitys just can macroscopically accumulate formation hydrodynamic effect, and then improve the lubricating condition of plunger coupled parts.
In order to comprehensive groove 22 and the effect of cavity 24, reach better lubrication and sealing effect, see Fig. 3 and Fig. 5, the maximum cup depth h3 of groove 22 and the ratio of radial clearance h2 are preferably in the scope of 0.5 to 6.7.Such as, in a kind of schematically mode of execution, the maximum cup depth h3 of groove 22 is 4 with the ratio of radial clearance h2.
Sealing surface due to plunger offers the groove 22 with concentration gradient, can in force feed stroke, the fuel oil in extruding groove 24, high pressure is produced between plunger 10 and plunger bushing 30, form a high-pressure sealing chamber, the High-pressure phase equilibria produced with force feed, thus realize the effect of sealing; When plunger 10 moves in plunger bushing 30, cavity 24 contributes between plunger 10 and plunger bushing 30, form the hydrodynamic lubrication oil film with certain thickness and bearing capacity, makes plunger 10 and plunger bushing 30 form contactless slip, greatly improves lubricating condition.Cavity 24 and the composite structure of the groove 22 of varying depth, improve lubrication and the sealing of plunger coupled parts simultaneously.
Be to be understood that, although this specification describes according to each embodiment, but not each embodiment only comprises an independently technological scheme, this narrating mode of specification is only for clarity sake, those skilled in the art should by specification integrally, technological scheme in each embodiment also through appropriately combined, can form other mode of executions that it will be appreciated by those skilled in the art that.
A series of detailed description listed is above only illustrating for possible embodiments of the present invention; they are also not used to limit the scope of the invention, all do not depart from the skill of the present invention Equivalent embodiments done of spirit or change all should be included within protection scope of the present invention.
Claims (6)
1. the plunger (10) of diesel injection pump, described plunger comprises a drive end (11), a force feed end (13) and a sealing surface (12), it is characterized in that:
Sealing face (12) offers many grooves (22), described groove (22) is 30 ° to 70 ° with the angle of the axis of described plunger, the area sum that each described groove (22) and described sealing surface (12) intersection are formed be the circumferential theoretical surface of described sealing surface (12) long-pending 5% to 35%, the degree of depth of each described groove (22) increases to close described drive end (11) place from it gradually near described force feed end (13);
Sealing face (12) is not offered described groove (22) place and is evenly equipped with cavity (24), the area sum that described cavity (24) and described sealing surface (12) intersection are formed be the circumferential theoretical surface of described sealing surface (12) amass 2% to 30%.
2. the plunger of diesel injection pump as claimed in claim 1, wherein said a plurality of grooves (22) are parallel to each other.
3. the plunger of diesel injection pump as claimed in claim 1, wherein the Elongation of each described groove (22) is 2 to 6.
4. the plunger of diesel injection pump as claimed in claim 1 is wherein 10 ° to 45 ° at the bottom land (23) of each described groove (22) with the tangential angle of described sealing surface (12) intersection.
5. the plunger of diesel injection pump as claimed in claim 3, wherein:
The width of each described groove (22) is 10 μm to 30 μm,
The diameter of each described cavity (24) is 10 μm to 50 μm.
6. the plunger coupled parts of diesel injection pump, it comprises:
A plunger (10) according to any one of claim 1 to 5; With
The plunger bushing (30) of a sheathed described plunger (10), has a radial clearance (h2) between itself and described plunger (10);
Wherein:
The maximum depth (h1) of described cavity (24) and the ratio of described radial clearance (h2) are 0.4 to 5.3,
The maximum cup depth (h3) of described groove (22) and the ratio of described radial clearance (h2) are 0.5 to 6.7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510491925.5A CN105065165B (en) | 2015-08-12 | 2015-08-12 | The plunger and plunger matching parts of diesel injection pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510491925.5A CN105065165B (en) | 2015-08-12 | 2015-08-12 | The plunger and plunger matching parts of diesel injection pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105065165A true CN105065165A (en) | 2015-11-18 |
| CN105065165B CN105065165B (en) | 2017-11-10 |
Family
ID=54494641
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510491925.5A Active CN105065165B (en) | 2015-08-12 | 2015-08-12 | The plunger and plunger matching parts of diesel injection pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105065165B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107559185A (en) * | 2016-06-30 | 2018-01-09 | 罗伯特·博世有限公司 | Plunger pump and plunger |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2077034U (en) * | 1990-09-15 | 1991-05-15 | 上海柴油机厂 | Trunk piston diesel spray pump |
| JPH04272468A (en) * | 1991-02-26 | 1992-09-29 | Toyota Central Res & Dev Lab Inc | Plunger of injection pump for alcoholic fuel |
| US5630953A (en) * | 1993-05-13 | 1997-05-20 | Maschinenfabrik Gehring Gmbh & Co. | Method of fine-machining a workpiece surface to be supplied with a lubricant during operation of the workpiece |
| CN1959091A (en) * | 2006-08-25 | 2007-05-09 | 王德恒 | Oil saving piston of internal-combustion engine |
| CN202108686U (en) * | 2011-05-18 | 2012-01-11 | 加西贝拉压缩机有限公司 | Piston applied on a compressor |
| CN204921226U (en) * | 2015-08-12 | 2015-12-30 | 江苏大学 | Plunger and plunger matching parts of diesel engine injection pump |
-
2015
- 2015-08-12 CN CN201510491925.5A patent/CN105065165B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2077034U (en) * | 1990-09-15 | 1991-05-15 | 上海柴油机厂 | Trunk piston diesel spray pump |
| JPH04272468A (en) * | 1991-02-26 | 1992-09-29 | Toyota Central Res & Dev Lab Inc | Plunger of injection pump for alcoholic fuel |
| US5630953A (en) * | 1993-05-13 | 1997-05-20 | Maschinenfabrik Gehring Gmbh & Co. | Method of fine-machining a workpiece surface to be supplied with a lubricant during operation of the workpiece |
| CN1959091A (en) * | 2006-08-25 | 2007-05-09 | 王德恒 | Oil saving piston of internal-combustion engine |
| CN202108686U (en) * | 2011-05-18 | 2012-01-11 | 加西贝拉压缩机有限公司 | Piston applied on a compressor |
| CN204921226U (en) * | 2015-08-12 | 2015-12-30 | 江苏大学 | Plunger and plunger matching parts of diesel engine injection pump |
Non-Patent Citations (1)
| Title |
|---|
| 尹必峰等: "缸套表面复合织构润滑性能理论及试验研究", 《西安交通大学学报》 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107559185A (en) * | 2016-06-30 | 2018-01-09 | 罗伯特·博世有限公司 | Plunger pump and plunger |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105065165B (en) | 2017-11-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104279055B (en) | Connecting rod for two-stage variable compression ratio | |
| JP2014137139A (en) | Sealing device and its use method | |
| CN202954965U (en) | Plunger with spiral lubricating oil grooves and used for inclined-disc-type axial plunger pump | |
| JP3234332U (en) | Fuel pump for direct injection system | |
| CN103939467A (en) | Air hydrostatic bearing of machine making free piston type reciprocating motion | |
| CN204921226U (en) | Plunger and plunger matching parts of diesel engine injection pump | |
| CN105065165A (en) | Plunger and plunger coupling piece of diesel engine fuel injection pump | |
| CN104131909A (en) | Piston of internal combustion engine | |
| JP2017203408A (en) | piston | |
| CN110925159B (en) | Axial plunger pump piston shoe of groove structure | |
| US11408385B2 (en) | Component, in particular fuel line or fuel distributor, and fuel injection system | |
| FI20215003A1 (en) | Multi-cylinder combined high pressure oil pump for marine low speed engine | |
| CN102434422B (en) | Pumping device and lubricating method thereof | |
| JP2008057527A (en) | Plunger pump | |
| CN107345516B (en) | Plunger sealing ring for high-pressure fuel pump and corresponding high-pressure fuel pump | |
| CN207715310U (en) | A kind of inclined plunger pump plunger and the bent axis type axial piston pump with the plunger | |
| CN211975367U (en) | Can improve lubricated effect's crosshead subassembly for diaphragm pump | |
| CN204436771U (en) | A kind of plunger pump swash plate | |
| CN204458081U (en) | Efficient burning piston | |
| CN205478270U (en) | Plunger pump seals packing subassembly | |
| CN205089512U (en) | Needle valve and needle valve idol piece of diesel engine fuel sprayer | |
| CN105065166A (en) | Needle valve of diesel engine oil nozzle , needle valve coupling piece and needle valve machining method | |
| CN205823774U (en) | A kind of differential off-load relief valve | |
| CN210623066U (en) | Connecting rod connecting ring for horizontally opposed plunger pump | |
| CN106337737B (en) | Bearing interface with grooves to reduce friction |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |