CN101094983A - Fuel supply pump - Google Patents
Fuel supply pump Download PDFInfo
- Publication number
- CN101094983A CN101094983A CNA2005800452667A CN200580045266A CN101094983A CN 101094983 A CN101094983 A CN 101094983A CN A2005800452667 A CNA2005800452667 A CN A2005800452667A CN 200580045266 A CN200580045266 A CN 200580045266A CN 101094983 A CN101094983 A CN 101094983A
- Authority
- CN
- China
- Prior art keywords
- valve
- fuel
- expulsion
- enter
- valve body
- 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.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/462—Delivery valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/464—Inlet valves of the check valve type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
A fuel supply pump having a valve that does not seizes up, that is highly reliable, and that is easily processed. A valve body (3) is formed by joining and integrating an inlet valve body (5) and an outlet valve body (6), a fuel container chamber (7) is formed at the joint, and an inlet valve (1) and an outlet valve (2) are arranged so as to hold the fuel container chamber (7) between them. Fuel is sucked into a plunger chamber (56A) through a suction path (5b), the inlet valve (1), the fuel container chamber (7), and a suction-cum-ejection path (5d), and on the other hand, compressed fuel from the plunger chamber (56A) is ejected through the suction-cum-ejection path (5d), the fuel container chamber (7), and the outlet valve (2).
Description
Technical field
The present invention relates to a kind of combustion engine fuel supply pump, particularly realized the combustion engine fuel supply pump of structure improvement etc.
Background technique
In the prior art, as this device, for example with high-pressure service pump and feed pump fuel feed pump, in particular as the device known (with reference to patent documentation 1) of the supply pump of common rail fuel injection device as the main composition key element.
In the high-pressure service pump that constitutes this fuel feed pump, use device: as entering/expulsion valve (hereinafter referred to as " inlet and discharge valve (IO valve) ") with this spline structure, on expulsion valve, be formed with patchhole, insert in the hole to be provided with at this and enter valve and spring, carry out the application of force by spring and make and to enter the inflow passage side application of force of valve to fuel, and expulsion valve and enter valve and set with being coaxial shape.
But, in aforesaid structure, because expulsion valve and enter valve and set with being coaxial shape, so consider from the viewpoints of guaranteeing to slide vertically such as smoothness, with do not adopt such structure that is coaxial shape configuration and compare, space between expulsion valve and the valve body, expulsion valve and the space that enters between the valve are bigger, therefore, and the problem that exists valve to reduce with respect to its original axioversion, sliding.
In addition, hold expulsion valve and use parts with the valve body that enters valve, and be formed with the bigger chamber in space in inside, but the processing operation that such space is set in the components interior of one needs labour and time, the result not only causes the monomer costliness as inlet and discharge valve, and causes problems such as fuel feed pump costliness.
Patent documentation 1: TOHKEMY 2003-184703 communique (2-5 page or leaf and Fig. 1-Fig. 6)
Summary of the invention
The present invention finishes in view of above-mentioned condition, and a kind of fuel feed pump that sliding is improved and reliability is high of valve is provided.
Another object of the present invention is to provide a kind of fuel feed pump with the easy and cheap valve of processing operation.
According to technological scheme of the present invention, the fuel feed pump that provides has the inlet and discharge valve that fuel is controlled from the discharge of this fuel compression chamber to the suction and the fuel of fuel compression chamber, above-mentioned inlet and discharge valve will enter valve body and discharge valve body integrated and be provided with on the valve body that forms and enter valve and expulsion valve, be formed with fuel-storage cell at the above-mentioned joining portion that enters valve body and expulsion valve, above-mentionedly enter valve and expulsion valve sets across this fuel-storage cell, and enter to be provided with between valve and the expulsion valve at this and make the above-mentioned valve that enters be landed in force application device on the seat surface, the above-mentioned valve that enters constitutes by being formed on the above-mentioned suction path that enters in the valve body fuel is sucked in the above-mentioned fuel compression chamber, on the other hand, above-mentioned expulsion valve constitutes compressed fuel in above-mentioned fuel compression chamber is discharged.
According to the present invention, enter valve and expulsion valve unlike the prior art, they are configured on the same axis, so with enter valve and expulsion valve and be the existing structure that coaxial shape sets and compare, can set the space that enters between valve and expulsion valve and the valve body less, therefore, can provide such fuel feed pump: prevent to cause greatly the reduction of the sliding of valve in action because of the space, improve reliability, and valve integral body has compared with prior art realized miniaturization.
In addition,,, play that to process the operation of path etc. at valve inner extremely easy so compare with the existing valve body that constitutes by parts because valve body uses two parts and becoming one, and the effect of cheap that can implement device.
Description of drawings
Fig. 1 is the amplification profile of the topology example of the inlet and discharge valve that uses in the fuel feed pump of expression embodiments of the present invention.
Fig. 2 is the part sectioned view of topology example of the fuel feed pump of expression embodiments of the present invention.
Fig. 3 is the structural drawing of topology example of the common rail fuel injection device of the expression fuel feed pump that uses embodiments of the present invention.
Label declaration
1: enter valve
1a: valve portion
1c: seat surface
2: expulsion valve
2a: valve portion
2c: seat surface
3: valve body
5: enter valve body
5b: suck the path
5d: suck and discharge the dual-purpose path
6: discharge valve body
7: fuel-storage cell
Embodiment
Below, referring to figs. 1 through Fig. 3 embodiments of the present invention are described.
In addition, below Shuo Ming parts and configuration etc. do not limit the present invention, can carry out various changes in the scope of purport of the present invention.
The fuel feed pump of embodiments of the present invention is applied to especially as in the employed device of the supply pump of common rail fuel injection device, and a topology example of common rail fuel injection device at first is described with reference to Fig. 3.
Common rail fuel injection device mainly is made of high-pressure service pump 101, feed pump 102, common rail 103 and a plurality of sparger 104, and its basic structure is known from prior art.In addition, the fuel feed pump P of embodiments of the present invention mainly is made of high-pressure service pump 101 and feed pump 102.
Utilize feed pump 102 to supply with high-pressure service pump 101 by filter 106 from the fuel that fuel tank 105 draws, with this fuel that is supplied to as described later to rail 103 force feeds altogether, on the other hand, the unnecessary fuel of supply returns fuel tank 105 by first or second return path 92,93.
In this high-pressure service pump 101, be provided with two plungers 56 that the driving force by motor (not shown) moves up and down, the volume of the 56A of plunger compartment of pressing chamber of acting as a fuel can change by moving up and down of this plunger 56, fuel flows among the 56A of each plunger compartment by the inlet and discharge valve 71 with the corresponding setting of the 56A of each plunger compartment difference, and passes through inlet and discharge valve 71 to being total to rail 103 force feeds from the 56A of plunger compartment like that as described later.
Be formed with supply passage 91 in high-pressure service pump 101, this supply passage 91 is provided with the proportional control valve 107 that is used to control from the fuel flow rate of feed pump 102 halfway, and is communicated with above-mentioned inlet and discharge valve 71, thereby to the 56A of plunger compartment fueling.
And then, being provided with two return paths that an end is connected together and be connected with fuel tank 105 in high-pressure service pump 101 is first and second return paths 92,93, the other end of first return path 92 be connected in supply passage 107 on the appropriate location of the input side of proportional control valve 107, on the other hand, the other end of second return path 93 be connected in supply passage 107 on the appropriate location between proportional control valve 107 and the inlet and discharge valve 71.
In addition, first return path 92 be provided with relief valve (over flow valve) 108 midway, in addition, be provided with throttle orifice 109 midway at second return path 93.
Fig. 2 is expression with the fuel feed pump P of an embodiments of the present invention sectional drawing when the axis of plunger 56 cuts, and with reference to this figure its institutional structure is described.In addition, in order to illustrate conveniently, in the explanation of a part with reference to Fig. 1.
In the pump case 51 of fuel feed pump P, pump case 51 relatively by under position (the paper bottom among Fig. 2) be formed with cam accommodating chamber 52, in cam accommodating chamber 52, dispose cam 53a, this cam 53a is arranged on the camshaft 53 of drive force of launched machine (not shown), and is formed with cylindrical 54 in the mode of extending upward from this cam accommodating chamber 52.In addition, plunger bushing 55 intercalations roughly cylindraceous are in cylindrical 54.
In plunger bushing 55, run through the valve receiving bore 55b that is provided with plunger receiving bore 55a and is communicated with in Fig. 2 with this plunger receiving bore 55a along its axial (being the above-below direction of paper).In addition, valve receiving bore 55b is positioned at the top of plunger receiving bore 55a in Fig. 2.
In addition, in plunger receiving bore 55a, can accommodate plunger 56 along the vertical direction slidably.
End at this plunger 56 is the end of camshaft 53 sides, is fixed with push rod 58 with spring bracket 57.
In addition, the position above spring bracket 57 is formed with annular projection 59 on the appropriate location of cylindrical 54, is equipped with piston spring 60 between this annular projection 59 and spring bracket 57, thereby makes plunger 56 pass through push rod 58 all the time to the cam 53a application of force.
On the other hand, in valve receiving bore 55b, accommodate inlet and discharge valve 71 in the mode that is assembled between valve holder 72 and the plunger bushing 55.That is, inlet and discharge valve 71 is with the mode intercalation that the is pressed bottom to valve receiving bore 55b, and an end that is set to valve holder 72 engages with the upper side (the paper upper side among Fig. 2) of inlet and discharge valve 71.Be formed with outside thread (omitting diagram) on the part of the periphery of this valve holder 72, this outside thread screws with the internal thread that is formed on week in the valve receiving bore 55b (omitting diagram), thereby valve holder 72 is tightened among the valve receiving bore 55b.
Inside at this valve holder 72, near the receiving bore 72a that inlet and discharge valve 71 sides have an opening is formed into the axial substantial middle of valve holder 72, and run through to be provided with drain passageway 72b in the inside of this valve holder 72, this drain passageway 72b is communicated with this receiving bore 72a and at open-ended (with reference to Fig. 1) of the opposition side of inlet and discharge valve 71.
Receiving bore 72a forms the size of such degree: constitute the end of expulsion valve 2 of inlet and discharge valve 71 described later and the inside (with reference to Fig. 1) that the 2a of valve portion can be positioned at receiving bore 72a with suitable surplus.
At the position that the bottom of this receiving bore 72a promptly is communicated with drain passageway 72b, intercalation has expulsion valve spring bracket 73.Run through to be provided with intercommunicating pore 73a at the middle body of this expulsion valve spring bracket 73, this intercommunicating pore 73a and previous drain passageway 72b have the diameter that equates substantially and are communicated with drain passageway 72b.In addition, elasticity is equipped with expulsion valve spring 74 between the 2a of valve portion of expulsion valve spring bracket 73 and expulsion valve 2, thereby makes expulsion valve 2 all the time to the seat surface 6c of the discharge valve body 6 described later application of force (with reference to Fig. 1).
In addition, drain passageway 72b is by rail 103 connections together of not shown pipe arrangement.
Fig. 1 represents the amplification profile of inlet and discharge valve 71, below describes inlet and discharge valve 71 in detail with reference to this figure.
The inlet and discharge valve 71 of embodiments of the present invention constitute have the valve of entering 1, expulsion valve 2, valve body 3 and enter valve spring 4.
At first, both constitute valve body 3 by entering valve body 5 and discharging valve body 6, by be engaged with each other, the fixing one that becomes.In addition, fixation method needn't be defined as specific method, and can use suitably that for example welding and screw thread are fixed etc.For example, in the present embodiment, by valve holder 72 screw threads are fixed on the inlet and discharge valve 71, enter valve body 5 and discharge that valve body 6 is bonded with each other and fixing, guarantee oil seal thus thereby make.
Near the substantial middle that enters valve body 5, longitudinally (the paper above-below direction among Fig. 1) be formed with enter that valve 1 can be slidably inserted into enter valve patchhole 5a.In addition, near this enters the bottom of valve patchhole 5a, suck path 5b being formed into the side that enters valve body 5 with the mode that enters valve patchhole 5a quadrature and, and suck path 5b and enter valve patchhole 5a and be communicated with at lateral opening.This suction path 5b is communicated with (with reference to Fig. 2) with supply passage 91 in being formed on plunger bushing 55.
Enter valve 1 and near an end of columnar part, be formed with the large diameter valve 1a of portion, and, be formed with a plurality of foliaceous guide portion 1b at the downside (the paper downside among Fig. 1) of the 1a of this valve portion, promptly on the periphery at the position of a side opposite with an end of columnar part.
Be formed with seat surface 1c near the periphery of the foliaceous guide portion 1b of the 1a of valve portion side, this seat surface 1c is by engaging with the seat surface 5c that is formed on the previous open part that enters valve patchhole 5a that enters valve body 5, enters valve 1 and is seated at seat surface 5c thereby can make.In addition, in embodiments of the present invention, above-mentioned foliaceous guide portion 1b forms the length of such degree: entering under the state that valve 1 is seated at seat surface 5c as shown in Figure 1, the lower end part of this foliaceous guide portion 1b is near the edge of the open part that sucks path 5b.
In addition, in entering valve body 5, enter valve patchhole 5a near, and enter valve patchhole 5a and run through concurrently to be provided with and suck to discharge dual-purpose path 5d, two ends of this suctions discharge dual-purpose path 5d are entering the upper and lower surface opening of valve body 5 respectively.As described later, the end opening that dual-purpose path 5d is discharged in this suction is entering valve body 5 and is discharging in the fuel-storage cell 7 that marks between the valve body 6, and on the other hand, another is distolateral to be communicated with the 56A of plunger compartment.
On the other hand, partly be formed with recess 6a in the substantial middle with entering valve body 5 mating faces of discharging valve body 6, the axial section shape entering valve 1 and expulsion valve 2 of this recess 6a is roughly trapezoidal.In addition, mark fuel-storage cell 7 by this recess 6a with the mating face that enters valve body 5.
In this fuel-storage cell 7, a previous described end and the 1a of valve portion that enters valve 1 is positioned at substantial middle, and suction is discharged the end of dual-purpose path 5d at these fuel-storage cell 7 split sheds.
And then expulsion valve patchhole 6b runs through setting in the mode that is communicated with this recess 6a to the opposition side that enters valve body 5, and expulsion valve 2 can insert among this expulsion valve patchhole 6b with being free to slide.That is, in embodiments of the present invention, enter valve 1 and expulsion valve 2 and be across fuel-storage cell 7 and be provided in structure on the same axis.
Expulsion valve 2 except its axial length slightly greater than previous entering the valve 1, basic shape with enter valve 1 and form identically.That is, be provided with the 2a of valve portion enter the end of opposition side of end of valve 1 side being positioned at of expulsion valve 2 near, and in the lower side of the 2a of this valve portion, promptly be positioned on the position that enters valve 1 side, along circumferentially being formed with a plurality of foliaceous guide portion 2b across appropriate intervals.
In addition, near the periphery of the foliaceous guide portion 2b of the 2a of valve portion side, be formed with seat surface 2c, this seat surface 2c engages with the seat surface 6c of the open part that is formed on expulsion valve patchhole 5a, the open part of described expulsion valve patchhole 5a is being discharged upper surface, the i.e. surperficial upper shed of an opposite side with the mating face that enters valve body 5 of valve body 6, thereby expulsion valve 2 is seated on the seat surface 6c.
And then between the end face of the foliaceous guide portion 2b of 1a of valve portion that enters valve 1 and expulsion valve 2, elasticity is equipped with as the spiral helicine valve spring 4 that enters of forming of force application device, thus, makes to enter valve 1 all the time to the seat surface 5c application of force that enters valve body 5.
Next the action of fuel feed pump P in the said structure, the particularly action of inlet and discharge valve 71 mainly are described.
When motor (not shown) when beginning to rotate, its driving force is transmitted by not shown mechanism and is made camshaft 53 rotations, cam 53a rotation simultaneously.Follow the rotation of cam 53a, push rod 58 moves up and down and plunger 56 moves up and down.
Though not shown, because feed pump 102 drives with camshaft 53 launched machines,, draw fuel from fuel tank 105 so camshaft 53 rotations and feed pump 102 also are driven, and with fuel supply high-pressure service pump 101.
For example, when plunger 56 from top dead center when lower dead center moves, the pressure of fuel-storage cell 7 descends, and acts on the back pressure that enters on the valve 1 and reduces, the pressure that sucks path 5b improves relatively.In addition, pressure in sucking path 5b surpasses when entering the elastic force of valve spring 4, enter valve 1 by on push away, fuel flows into to suck path 5b and be full of by supply passage 91 from feed pump 102 and sucks path 5b, this fuel by at the seat surface 1c that is formed at the 1a of valve portion that enters valve 1 with enter in the gap inflow fuel-storage cell 7 that produces between the seat surface 5c of valve body 5.Then, the fuel that flow in the fuel-storage cell 7 is discharged among the dual-purpose path 5d inflow 56A of plunger compartment by sucking, thereby to the 56A of plunger compartment fueling.This state continuance arrives lower dead center to plunger 56.
Next, when plunger 56 when lower dead center is moved upward, the pressure of fuel-storage cell 7 rises, and acts on the back pressure that enters on the valve 1 and raises, the pressure that sucks path 5b reduces relatively.Therefore, with suck path 5b in fuel on be advanced into valve 1 power compare, act on the bigger with joint efforts of back pressure that enters on the valve 1 and the active force that enters valve spring 4, so the seat surface 1c that is formed on the 1a of valve portion that enters valve 1 is pressed against on the seat surface 5c that enters valve body 5, suck path 5b thereby close.That is, in other words, suck path 5b and be cut off with being communicated with of fuel-storage cell 7.
Close when sucking path 5b, when plunger 56 continued to be moved upward, the pressure of fuel-storage cell 7 continued to rise, and acted on back pressure on the expulsion valve 2 greater than the pressure in the downstream side of active force that is configured in the expulsion valve spring 74 in the valve holder 72 and expulsion valve 2.In addition, here, the downstream side of so-called expulsion valve 2 is meant that the ratio of expulsion valve 2 is arranged in the close position of rail 103 sides altogether of the 2a of valve portion of the receiving bore 72a of valve holder 72.
Its result is, the seat surface 2c that is formed on the 2a of valve portion of expulsion valve 2 leaves from the seat surface 6c that discharges valve body 6, sucks to discharge dual-purpose path 5d and open.Promptly, in the 56A of plunger compartment pressurized fuel by suck between seat surface 2c that discharges dual-purpose path 5d, fuel-storage cell 7, the 2a of valve portion and the seat surface 6c that discharges valve body 6, receiving bore 72 and the intercommunicating pore 73a of expulsion valve spring bracket 73 and the drain passageway 72b of valve holder 72 of valve holder 72, supply with and be total to rail 103.This state continuance arrives top dead center to plunger 56.
Supply with the fuel that is total to rail 103 and distribute to each sparger 104, sparger 104 carries out fuel based on the control of not shown control device to motor (not shown) and sprays.
In addition, the amount of supplying with the fuel of the 56A of plunger compartment from feed pump 102 is that the control of the fuel flow rate of passing ratio control valve 107 unit time of being carried out is regulated.
The flow control that passing ratio control valve 107 is carried out, unnecessary fuel returns fuel tank 105 in the side nearby of proportional control valve 107 by first return path 92.At this, in first return path 92, be provided with relief valve 108, this relief valve 108 is normally opens, so supply passage 91 remains pressure in the prespecified range at the pressure from proportional control valve 107 to upstream side.
In addition, because proportional control valve 107 can not cut off flowing of fuel fully under full-shut position, so fuel leaks to the supply passage 91 in proportional control valve 107 downstream sides, still, the fuel of this leakage returns fuel tank 105 by second return passage 93 and first return passage 92.In addition, second return passage 93 of flowing through maintains in the predetermined value by the throttle orifice 109 that is arranged in this second return passage 93 to the flow of the unit time of returning fuel that fuel tank 105 returns.
Utilizability on the industry
Fuel feed pump of the present invention can be applied to the supply pump of common rail fuel injection device, spy Be not suitable for realizing miniaturization and the cheap of fuel injection device.
Claims (6)
1, a kind of fuel feed pump, this fuel feed pump have the inlet and discharge valve that fuel is controlled from the discharge of this fuel compression chamber to the suction and the fuel of fuel compression chamber, it is characterized in that,
Above-mentioned inlet and discharge valve will enter valve body and discharge valve body integrated and be provided with on the valve body that forms and enter valve and expulsion valve,
Be formed with fuel-storage cell at the above-mentioned joining portion that enters valve body and expulsion valve, above-mentionedly enter valve and expulsion valve sets across this fuel-storage cell, and enter to be provided with between valve and the expulsion valve at this and make the above-mentioned valve that enters be landed in force application device on the seat surface,
The above-mentioned valve that enters constitutes by being formed on the above-mentioned suction path that enters in the valve body fuel is sucked in the above-mentioned fuel compression chamber, and on the other hand, above-mentioned expulsion valve constitutes discharges compressed fuel in above-mentioned fuel compression chamber.
2, fuel feed pump according to claim 1 is characterized in that,
In entering valve body, be formed with an end at the fuel-storage cell opening and the other end is discharged the dual-purpose path in the suction of fuel compression chamber opening, and in entering valve body, also be formed with above-mentioned fuel-storage cell split shed and slidably hold freely above-mentioned enter valve enter the valve patchhole, suck path and enter the valve patchhole with this and be communicated with.
3, fuel feed pump according to claim 2 is characterized in that,
Be formed with the expulsion valve patchhole in discharging valve body, an end of this expulsion valve patchhole is at the fuel-storage cell split shed, and the other end is at the outside opening of valve body, inserts in the hole at this expulsion valve and can hold expulsion valve with being free to slide.
4, fuel feed pump according to claim 3 is characterized in that,
Be formed with large diameter valve portion on the valve entering, this valve portion is arranged in fuel-storage cell, and is set to be landed on the seat surface that is formed at the opening periphery that enters the valve patchhole.
5, fuel feed pump according to claim 4 is characterized in that,
Be formed with large diameter valve portion on expulsion valve, this valve portion is positioned at the outside of valve body, and is set to be landed on the seat surface of the opening periphery that is formed at the expulsion valve patchhole.
6, fuel feed pump according to claim 5 is characterized in that,
On the position that the expulsion valve that is positioned at valve subordinate side of expulsion valve inserts in the hole, be formed with a plurality of foliated positions along its peripheral direction, in the end at this foliated position and enter between the valve portion of valve, elasticity is equipped with uses helical spring force application device.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004381381A JP2006183647A (en) | 2004-12-28 | 2004-12-28 | Fuel supply pump |
| JP381381/2004 | 2004-12-28 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101094983A true CN101094983A (en) | 2007-12-26 |
Family
ID=36614836
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2005800452667A Pending CN101094983A (en) | 2004-12-28 | 2005-12-26 | Fuel supply pump |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2006183647A (en) |
| CN (1) | CN101094983A (en) |
| WO (1) | WO2006070719A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013026273A1 (en) * | 2011-08-25 | 2013-02-28 | Bosch Automotive Diesel Systems Co., Ltd. | Fluid inlet/outlet valve for use in a high pressure fluid pump |
| CN107989730A (en) * | 2017-12-28 | 2018-05-04 | 北京亚新科天纬油泵油嘴股份有限公司 | A kind of high voltage common rail pump and for its into oil outlet valve component |
| CN110366639A (en) * | 2017-02-28 | 2019-10-22 | 株式会社三国 | Pump installation |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010031390B4 (en) * | 2010-07-15 | 2018-08-09 | Man Diesel & Turbo Se | Suction valve of a fuel supply system of an internal combustion engine |
| WO2012020466A1 (en) | 2010-08-09 | 2012-02-16 | ボッシュ株式会社 | High pressure pump |
| CN103114947A (en) * | 2013-02-06 | 2013-05-22 | 福建省莆田市中涵机动力有限公司 | Common rail pump oil inlet and outlet combination valve |
| CN104018968B (en) * | 2013-03-01 | 2019-04-23 | 罗伯特·博世有限公司 | High-pressure fuel-feed pump and diesel engine with this high-pressure fuel-feed pump |
| DE102013209021A1 (en) * | 2013-05-15 | 2014-11-20 | Robert Bosch Gmbh | Pump, in particular high-pressure fuel pump of an internal combustion engine |
| DE102013226953B4 (en) * | 2013-12-20 | 2016-10-06 | Robert Bosch Gmbh | High pressure pump with a valve piece |
| CN206320002U (en) * | 2016-10-14 | 2017-07-11 | 罗伯特·博世有限公司 | High-pressure plunger pump and its high potential assembly, inlet valve |
| JP7412065B2 (en) | 2019-03-05 | 2024-01-12 | ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング | high pressure pump |
| CN111894780B (en) * | 2020-07-30 | 2022-06-21 | 一汽解放汽车有限公司 | Oil inlet valve for oil supply pump and high-pressure common rail system |
| JP2023008576A (en) * | 2021-07-06 | 2023-01-19 | 三菱重工エンジン＆ターボチャージャ株式会社 | Fuel pump |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH399072A (en) * | 1963-01-21 | 1966-03-31 | Sulzer Ag | Fuel injection pump for a piston internal combustion engine |
| DE19541507A1 (en) * | 1995-11-08 | 1997-05-15 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
| JP2003184703A (en) * | 2001-12-21 | 2003-07-03 | Bosch Automotive Systems Corp | Fuel feed pump |
-
2004
- 2004-12-28 JP JP2004381381A patent/JP2006183647A/en active Pending
-
2005
- 2005-12-26 WO PCT/JP2005/023738 patent/WO2006070719A1/en not_active Application Discontinuation
- 2005-12-26 CN CNA2005800452667A patent/CN101094983A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013026273A1 (en) * | 2011-08-25 | 2013-02-28 | Bosch Automotive Diesel Systems Co., Ltd. | Fluid inlet/outlet valve for use in a high pressure fluid pump |
| CN110366639A (en) * | 2017-02-28 | 2019-10-22 | 株式会社三国 | Pump installation |
| CN110366639B (en) * | 2017-02-28 | 2021-05-04 | 株式会社三国 | Pump device |
| CN107989730A (en) * | 2017-12-28 | 2018-05-04 | 北京亚新科天纬油泵油嘴股份有限公司 | A kind of high voltage common rail pump and for its into oil outlet valve component |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2006070719A1 (en) | 2006-07-06 |
| JP2006183647A (en) | 2006-07-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101094983A (en) | Fuel supply pump | |
| JP3737355B2 (en) | High pressure injection system with common rail | |
| RU2631588C2 (en) | Injector for lubrication oil injection to engine cylinders and its application | |
| EP2013471B1 (en) | High-pressure fuel delivery device | |
| CN101868614B (en) | Safety valve and high-pressure pump comprising the safety valve | |
| US4485787A (en) | Fuel injection system | |
| US8136741B2 (en) | Fuel injection device for an internal combustion engine using direct fuel injection | |
| US20070251499A1 (en) | High-Pressure Pump for a Fuel Injection System of an Internal Combustion Engine | |
| US10851753B2 (en) | Fuel injector, a fuel injector assembly and an associated method | |
| CN107120219B (en) | High-pressure oil pump and engine | |
| DE112016005545B4 (en) | Pressure relief valve device and high pressure pump using the same | |
| KR20020091220A (en) | High-pressure fuel feed pump | |
| US7096856B2 (en) | Fuel feed pump for internal combustion engines | |
| KR102268857B1 (en) | fuel pump | |
| US20140182550A1 (en) | Quill with Integrated Flow Limiter | |
| EP2492492A1 (en) | Pumping head | |
| US20020073966A1 (en) | Fuel injection system for internal combustion engines | |
| CN202545080U (en) | Electrically-controlled plunger and barrel assembly of high-pressure oil pump | |
| CN208330601U (en) | Plunger pump and high pressure fuel pump | |
| KR20010101605A (en) | Injector for high-pressure fuel injection | |
| CN107587964A (en) | The petrolift with improved maximum pressure valve suitable for direct-injection system | |
| JP2860519B2 (en) | Engine stop device for diesel engine | |
| JP2010121452A (en) | Fuel supply pump | |
| JP2000297726A (en) | Fuel supply system | |
| CN1089850C (en) | Fuel injection pump for inernal-combustion engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |