CN104775957B - High-pressure fuel feed pump and the release valve unit for the pump - Google Patents
High-pressure fuel feed pump and the release valve unit for the pump Download PDFInfo
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- CN104775957B CN104775957B CN201510088756.0A CN201510088756A CN104775957B CN 104775957 B CN104775957 B CN 104775957B CN 201510088756 A CN201510088756 A CN 201510088756A CN 104775957 B CN104775957 B CN 104775957B
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Abstract
The present invention provides a kind of high-pressure fuel feed pump and the release valve unit for it for being equipped with mitigating the dump valve of the influence of noise caused by the circumferential The fuel stream of valve body.High-pressure fuel feed pump has the dump valve as check-valves between compression chamber and outlet.Dump valve is made up of valve housing, discharge valve spring, valve body and seat component.Dump valve is flap type.During valve opening, from compression chamber from the flowing for the fuel for axially having crashed into valve body, as the radial direction of valve body with it is radial it is scattered, directly flow to the The fuel stream of tap and crashing into the circumferential The fuel stream for the valve body that tap is flowed to after the inwall of valve casing.Dump valve, which has, to be formed between the periphery of present component and the periphery of valve body and the inner circumferential of valve casing, for the liquid damper chamber of circumferential The fuel stream.Liquid damper chamber is made up of first, second, third annular interstice.
Description
The present patent application is Application No. 200980156950.0 (international application no is PCT/JP2009/053077), Shen
Please day it be on 2 20th, 2009, the invention of entitled " high-pressure fuel feed pump and the release valve unit for the pump " is special
The divisional application of profit application.
Technical field
Discharge the present invention relates to the high-pressure fuel feed pump for supplying fuel to engine under high pressure and for the pump
Valve cell, is more particularly to suitable for preventing the high-pressure fuel feed pump of the flutter of dump valve and the dump valve list for the pump
Member.
Background technology
Typically in the device pressurizeed to fluid, the compression motion cause collision sound, as pressure fluctuation sound respectively
Plant noise.The pressure fluctuation that there occurs is absorbed with oil buffers such as accumulators or sound insulation is used in contrast, taking
Material carries out absorbing such countermeasure to the noise that there occurs, but due to the countermeasure for post processing, so, from space saving, low
It is unfavorable from the viewpoint of cost.
Therefore, for these shortcomings, it investigated the valve arrangement that low noise function is set in valve cell.
For example, first, from multiple taps in valve casing are formed towards in the check valve of the composition of radial direction discharge fuel,
Know the valve arrangement (referring for example to patent document 1) for being provided with buffer part, after by tap, the pressure of working solution is by the buffering
Row buffering is entered in portion.
In addition, second, known such valve arrangement (referring for example to patent document 2) in check valve, the valve arrangement is to make
The direction change of the discharge stream flowed from valve seat to tap is small and valve seat is steadily formed as taper by flowing, on valve body
There is provided the conus portion taken a seat on valve seat.
Patent document 1：Japanese Patent Publication 5-66275 publications
Patent document 2：Japanese Patent Publication 5-22969 publications
The content of the invention
The disclosure of invention
Problems to be solved by the invention
In the valve for the composition that patent document 1, patent document 2 are recorded, from the The fuel stream for axially crashing into valve body during valve opening
Disperseed in the radial direction of valve body with radial.Wherein, the The fuel stream for foring the scope of tap directly flows to tap, as valve
The The fuel stream of body radial direction.On the other hand, the The fuel stream for the scope for not forming tap is flowed to after the inwall of valve casing is crashed into, and is flowed
Toward tap, as the circumferential The fuel stream of valve body.
In the valve that patent document 1, patent document 2 are recorded, the The fuel stream for the scope for not forming tap is flowed in valve body
Circumference turn into high pressure, the The fuel stream of high speed, the influence to valve body movement can not ignore, and produce the variation for causing pressure fluctuation
(hereinafter referred to as flutter).
In addition, generally, although also can less even if the axial internal clearance of valve body using the ball valve of spherical valve body
The discharge rate of larger flow is obtained, but the axial amount of movement of valve body and the relation of discharge rate are non-rectilinear.In contrast, flat
In plate valve, the axial amount of movement of valve body and the relation of discharge rate are straight line.Herein, flap type is such valve, the valve
The surface of the valve seat of valve body is parallel to the plane orthogonal with the axial direction of valve body, in addition, the surface for the portions that valve body is abutted is also parallel
In the plane orthogonal with the axial direction of valve body.The valve that patent document 1 is recorded is flap type.However, in flap type, it is big in order to discharge
Flow is, it is necessary to increase the axial amount of movement of valve body.There is gap, such as valve sliding between the valve housing and valve body that keep valve body
Body is diametrically offset from the center of valve housing, then the sectional area that circumferential fuel stream passes through produces big difference in the both sides of valve body
Not.As a result, the differential pressure increase of valve body is acted on, as vibromotive force, flutter is produced.Flutter is axially moved in the valve body of valve body
It is easier when momentum is bigger to occur, easily become a problem in the flap type of discharge big flow.
Flutter is the vibration in the direction vertical with the open and close valve direction of action of valve body, once occur, then the combustion around valve body
Material can be affected, and occur pressure fluctuation.The pressure fluctuation so occurred is propagated by piping system, amplified, and is become noise and is put
Go out to outside, the problem of there is generation noise.
It is equipped with mitigating the noise as caused by valve body circumferential The fuel stream it is an object of the invention to provide a kind of
The high-pressure fuel feed pump of the dump valve of influence and the release valve unit for the pump.
The means used to solve the problem
(1) in order to achieve the above object, high-pressure fuel feed pump of the invention has makes volume by the reciprocating action of plunger
The compression chamber of change, discharges the outlet of fuel pressurizeed by the compression chamber, and be located at the outlet and above-mentioned compression chamber it
Between the dump valve as check-valves；The dump valve is made up of valve housing, valve body and seat component, and the valve housing is formed with connection
To multiple taps of above-mentioned outlet, the valve body is housed in the inside of the valve housing and closed by discharge valve spring by valve
Direction force, this component is housed in the inside of above-mentioned valve housing and with the seat that is abutted with above-mentioned valve body and close valve
Portion；Wherein：The surface of above-mentioned dump valve, the surface for the valve seat being formed on above-mentioned valve body and above-mentioned portions parallel to it is above-mentioned
The flap type of the orthogonal plane in the axial direction of valve body；When valve opening, from above-mentioned compression chamber by the hollow part of above-mentioned seat component from axle
To the flowing for the fuel for having crashed into above-mentioned valve body, as the radial direction in above-mentioned valve body with it is radial it is scattered, directly flow to it is above-mentioned
The The fuel stream of tap and flowed to after the inwall of valve casing has been crashed into tap valve body circumferential The fuel stream；The dump valve
With formation between the inner circumferential of the periphery and above-mentioned valve casing of the periphery of above-mentioned seat component and above-mentioned valve body, for above-mentioned circumferential
The liquid damper chamber of The fuel stream.
According to this composition, the influence of the noise as caused by valve body circumferential The fuel stream can be mitigated.
(2) in above-mentioned (1), best aforesaid liquid surge chamber has the first tubular conduit and the second tubular conduit；This
The formation of one tubular conduit is between the inner circumferential of the periphery of above-mentioned valve body and above-mentioned valve casing；Second tubular conduit formation is in above-mentioned seat
Between the inner circumferential of the periphery of component and above-mentioned valve casing.
(3) in above-mentioned (2), preferably first and second above-mentioned tubular conduit is made, in the axle comprising above-mentioned valve body
The sectional area of above-mentioned second tubular conduit in plane is bigger than the sectional area of above-mentioned first tubular conduit.
(4) in above-mentioned (3), the external diameter of above-mentioned valve body is preferably made bigger than the external diameter of above-mentioned valve seat.
(5) in above-mentioned (4), preferably by the formation of above-mentioned first tubular conduit in the outer of the above-mentioned valve seat located at above-mentioned valve body
Between the circular cone in week and the inner circumferential of above-mentioned valve casing.
(6) in above-mentioned (2), preferably make the sectional area α of above-mentioned fluid passage relative to above-mentioned dump valve standard-sized sheet when
Aperture area β turns into 0.1 × β of α ＞.
(7) in above-mentioned (1), the section in the plane of the axle comprising above-mentioned valve body of aforesaid liquid surge chamber is preferably made
Product is more than 0.3mm2。
(8) in addition, in order to achieve the above object, release valve unit of the invention is used for high-pressure fuel feed pump, the high pressure
Fuel feed pump discharges the fuel pressurizeed by compression chamber from outlet via the dump valve as check-valves, the dump valve list
Member is pressed into the inside of the valve housing for the part for constituting above-mentioned dump valve；Wherein：Above-mentioned release valve unit is by valve body and seat
Component is constituted, and the valve body is exerted a force by discharge valve spring in the direction of closing valve, this component have abutted with the valve body and incite somebody to action
The portions that valve is closed；The surface of above-mentioned dump valve, the surface for the valve seat being formed on above-mentioned valve body and above-mentioned portions parallel to
The flap type of the plane orthogonal with the axial direction of above-mentioned valve body；When valve opening, from above-mentioned compression chamber by the hollow of above-mentioned seat component
Portion is from the flowing of the fuel for axially having crashed into above-mentioned valve body, as the radial direction in above-mentioned valve body with radial scattered, direct stream
Toward above-mentioned tap The fuel stream and crashing into the circumferential The fuel stream for the valve body that tap is flowed to after the inwall of valve casing；Should
Dump valve, which has, to be formed between the periphery in above-mentioned seat component and the periphery of above-mentioned valve body and the inner circumferential of above-mentioned valve casing, for above-mentioned
The liquid damper chamber of circumferential The fuel stream.
According to this composition, the influence of noise caused by the circumferential The fuel stream of valve body can be mitigated.
The effect of invention
According to the present invention, the influence of noise caused by the circumferential The fuel stream of valve body can be mitigated.
Brief description of the drawings
Fig. 1 is the entirety of the high pressure fuel supply system of the high-pressure fuel feed pump of the 1st embodiment using the present invention
Pie graph.
Fig. 2 regards to represent to be used for the vertical profile of the composition of the dump valve of the high-pressure fuel feed pump of first embodiment of the present invention
Figure.
Fig. 3 regards to represent to be used for the vertical profile of the composition of the dump valve of the high-pressure fuel feed pump of first embodiment of the present invention
Figure.
Fig. 4 wants portion to put for expression for the composition of the dump valve of the high-pressure fuel feed pump of first embodiment of the present invention
Big sectional view.
Fig. 5 A are saying for the flowing for the fuel in the dump valve of the high-pressure fuel feed pump of first embodiment of the present invention
Bright figure.
Fig. 5 B are saying for the flowing for the fuel in the dump valve of the high-pressure fuel feed pump of first embodiment of the present invention
Bright figure.
Fig. 6 A are the explanation figure of the measurement result of the discharge pressure of the high-pressure fuel feed pump of first embodiment of the present invention.
Fig. 6 B are the explanation figure of the measurement result of the discharge pressure of the high-pressure fuel feed pump of first embodiment of the present invention.
Fig. 7 A are the release valve unit of the dump valve of high-pressure fuel feed pump of the expression as first embodiment of the present invention
The sectional view of composition.
Fig. 7 B are the release valve unit of the dump valve of high-pressure fuel feed pump of the expression as first embodiment of the present invention
The sectional view of composition.
Fig. 8 regards to represent to be used for the vertical profile of the composition of the dump valve of the high-pressure fuel feed pump of second embodiment of the present invention
Figure.
Fig. 9 regards to represent to be used for the vertical profile of the composition of the dump valve of the high-pressure fuel feed pump of third embodiment of the present invention
Figure.
Description of reference numerals
1 ... pump case
1a, 1b ... circumference end difference
2 ... plungers
8 ... dump valves
8A ... seat components
8A1 ... flange parts
8A2 ... end differences
8a ... portions
8b ... valve bodies
8b1 ... recesses
8b2 ... valve seats
8c ... discharges valve spring
8d ... valve housings
8d1 ... is oriented to side face
8d2 ... cutting planes portion
8d3 ... flange parts
8d4 ... balancing orifices
8d5 ... guide parts
8d6 ... end differences
9 ... pressure fluctuations mitigate mechanism
10c ... suction passages
11 ... compression chambers
13 ... outlets
20 ... fuel tanks
23 ... common rails
24 ... injectors
26 ... pressure sensors
27…ECU
30 ... electromagnetic suction valve mechanisms
801st, 807 ... taperings
802 ... end differences
803A, 803B ... tap
805 ... liquid damper chambers
805A, 805B, 805C ... tubular conduit
Embodiment
Below, composition and the action of the high-pressure fuel feed pump of the 1st embodiment of the present invention are illustrated using Fig. 1~Fig. 7.
Initially, the structure of the high pressure fuel supply system of the high-pressure fuel feed pump using present embodiment is illustrated using Fig. 1
Into.
Fig. 1 is the entirety of the high pressure fuel supply system of the high-pressure fuel feed pump of the 1st embodiment using the present invention
Pie graph.
In Fig. 1, the part surrounded by dashed line represents the pump case 1 of high-pressure fuel feed pump, will be by representing interrupted at this
Mechanism and part in line are integratedly encased in the high-pressure fuel feed pump for wherein constituting present embodiment.In addition, in figure,
Dotted line represents the flowing of electric signal.
Fuel in fuel tank 20 is drawn up by petrolift 21, by sucking pipe arrangement 28, is sent to the fuel suction port of pump case 1
10a.The fuel for having passed through fuel suction port 10a mitigates mechanism 9, suction passage 10c by pressure fluctuation, and reaching composition capacity can
Become the inlet hole 30a of the electromagnetic suction valve mechanism 30 of mechanism.
Electromagnetic suction valve mechanism 30 has magnet coil 30b.In the state of magnet coil 30b energizations, electromagnetic plunger 30c
Compression spring 33, as the state moved to Fig. 1 right, and maintains the state.Now, installed in electromagnetic plunger 30c's
The suction inlet 32 that the suction valve body 31 of front end will be communicated to the compression chamber 11 of high-pressure fuel feed pump is opened.In magnet coil 30b
For the state being not powered on, when there is no fluid differential pressure between suction passage 10c (inlet hole 30a) and compression chamber 11, by the bullet of spring 33
Property power to valve closing direction (left in Fig. 3) to suction valve body 31 exert a force, suction inlet 32 turn into close state, and maintain should
State.Fig. 1 represents the state that suction inlet 32 has been closed.
In compression chamber 11, plunger 2 can slidably be kept in Fig. 1 above-below direction.By the cam of internal combustion engine
When rotation makes plunger 2 to Fig. 1 lower section generation displacement in inhalation process state, the volume increase of compression chamber 11 is therein
Fuel pressure declines.In the process, as the fuel pressure in compression chamber 11 becomes than suction passage 10c (inlet hole 30a)
Pressure is lower, then producing valve opening force from the fluid differential pressure of fuel in suction valve body 31 (makes suction valve body 31 be moved to Fig. 1 right
Power).By the valve opening force, suction valve body 31 is overcome the elastic force valve opening of spring 33, open suction inlet 32.In this condition,
The control signal from ECU27 is such as applied to electromagnetic suction valve mechanism 30, then electric current flows to the electricity of electromagnetic suction valve mechanism 30
Magnetic coil 30b, makes electromagnetic plunger 30c be moved to Fig. 1 right, has been maintained open the state of suction inlet 32 from magnetic force.
The application state that such as maintain input voltage in electromagnetic suction valve mechanism 30 makes plunger 2 be transferred to pressure from inhalation process
Contracting process (from lower starting point to the rising process upper starting point), then due to maintain the "on" position to magnet coil 30b, institute
So that magnetic force is maintained, and suction valve body 31 still maintains the state of valve opening.The volume of compression chamber 11 is with the compression of plunger 2
Move and reduce, in this condition, be once inhaled into the fuel of compression chamber 11 again by the suction valve body of valve opening state
Between 31 and suction inlet 32, suction passage 10c (inlet hole 30a) is returned to, so, the pressure of compression chamber 11 will not rise.Should
Process is referred to as returning to process.
In process is returned, such as energization of the cut-out to magnet coil 30b then acts on electromagnetic plunger 30c magnetic force one
Disappeared after fixing time (after magnetic, machinery time delay).So, the bullet for the spring 33 for acting on suction valve body 31 always is utilized
Property power and from suction inlet 32 the pressure loss produce fluid force make left from suction valve body 31 to Fig. 1 move, close suction inlet
32.Such as suction inlet 32 is closed, then the fuel pressure from this in compression chamber 11 rises with the rising of plunger 2.Then, plus
When fuel pressure in pressure chamber 11 has exceeded the pressure of defined value bigger than the fuel pressure of outlet 13, compression chamber 11 is remained in
In fuel by dump valve 8 enter horizontal high voltage discharge, be fed into common rail 23.The process is referred to as to discharge process.As described above that
Sample, the compression section of plunger 2 includes returning to process and discharge process.
In process is returned, by having returned to the fuel in suction passage 10c in suction passage generation pressure fluctuation, but should
Pressure fluctuation be only from fuel suction port 10a to suction pipe arrangement 28 it is very micro ground adverse current, the return of fuel largely by pressure
Pulsation mitigates mechanism 9 and absorbed.
ECU27 controls the opportunity that the energization of from the electromagnetic plunger 30c to electromagnetic suction valve mechanism 30 is released, so as to control
The amount of the fuel under high pressure of discharge.The opportunity for such as releasing the energization to magnet coil 30b shifts to an earlier date, then reduces returning in compression section
Return the ratio of process, the ratio of increase discharge process.That is, the fuel for returning to suction passage 10c (inlet hole 30a) is reduced, is increased
The fuel of many high pressure discharges.In contrast, the opportunity for such as releasing above-mentioned energization postpones, then increase the return work in compression section
The ratio of sequence, reduces the ratio of discharge process.That is, increase returns to suction passage 10c fuel, reduces the combustion of high pressure discharge
Material.The opportunity that above-mentioned energization is released is from ECU27 by instruction control.
As described above, ECU27 controls the opportunity that the energization of magnet coil is released, and the fuel quantity that can make high pressure discharge is
The amount that internal combustion engine needs.
In pump case 1, in the row of setting between outlet (discharge side tubing connection portion) 13 of the outlet side of compression chamber 11
Go out valve 8.Dump valve 8 is made up of portions 8a, valve body 8b, discharge valve spring 8c and valve housing 8d.In compression chamber 11 and outlet 13
Between there is no a differential pressure of fuel in the state of, valve body 8b is crimped on portions 8a by discharge valve spring 8c elastic force, as valve closing
State.When fuel pressure in compression chamber 11 has exceeded the pressure of defined value bigger than the fuel pressure of outlet 13, valve body 8b
Fuel in resistance discharge valve spring 8c valve opening, compression chamber 11 is discharged to outlet 13 by dump valve 8.
After valve body 8b valve opening, the block 805 to be formed on valve housing 8d is such as touched, then action is restricted.In addition, valve
Body 8b stroke is suitably determined by valve housing 8d.Such as stroke is excessive, then valve body 8b closing delay makes to be discharged to outlet 13
Fuel again reflux in compression chamber 11, so, be used as the efficiency of high-pressure pump to decline.In addition, when valve body 8b repeats out
When valve and valve closing motion, guided in the way of being smoothly moved in stroke directions by valve housing 8d inwall 806.By such as with
On constitute like that, dump valve 8 turn into limitation fuel circulating direction check-valves.The detailed composition of dump valve 8 uses Fig. 2~figure
5 are explained below.
As described above, fuel suction port 10a fuel is directed in the compression chamber 11 of pump case 1 by plunger
Necessary amount is pressurizeed into high pressure by 2 reciprocating motion, and the common rail as high press fit pipe is sent to from outlet 13 by dump valve 8
23。
In addition, it is so far, illustrate to use in no power for closed valve state, when being powered as the normal of valve opening state
The example of the magnetic valve of closed form, but can also use in contrast to this in no power be valve opening state, be powered when be valve closing shape
The magnetic valve of the open type of state.In the occasion, the flow control instruction from ECU27 realizes reverse by switching on and off.
Injector 24 and pressure sensor 26 are installed in common rail 23.The number of cylinders that injector 24 corresponds to internal combustion engine is pacified
Dress, makes injector 24 that action is opened and closed, by the fuel injection of ormal weight to cylinder according to ECU27 control signal.
Below, the composition of the dump valve of the high-pressure fuel feed pump for present embodiment is illustrated using Fig. 2 and Fig. 3.
Fig. 2 and Fig. 3 is expression for the vertical of the composition of the dump valve of the high-pressure fuel feed pump of first embodiment of the present invention
Sectional view.In Fig. 2 and Fig. 3, if the moving direction of valve is Z axis, axle orthogonal to Z-axis is respectively X-axis, Y-axis.Fig. 2 is flat for Z-Y
Longitudinal section on face, Fig. 3 is the longitudinal section in Z-X planes.In addition, Fig. 2, Fig. 3 represent the valve opening state of dump valve.In figure
In 2 and Fig. 3, same section is represented with Fig. 1 identical symbols.
Dump valve 8 has the portions 8a illustrated in Fig. 1, valve body 8b, discharge valve spring 8c and valve housing 8d.Portions 8a,
Valve body 8b, discharge valve spring 8c and valve housing 8d are made of metal.Portions 8a forms present component 8A one end.Valve body
Shell 8d and seat component 8A are pressed into and are fixed on the inside of metal pump case 1.Valve body 8b is maintained in the way of it can slide
Valve housing 8d inside.In figure, Z-direction is valve body 8b glide direction.The row of insertion between valve body 8b and valve housing 8d
Go out valve spring 8c.Discharge valve spring 8c and flow into direction in opposite direction to valve body 8b forces with fuel.As illustrated in Figure 1 that
Sample, compression chamber 11 is located at the inside of pump case 1.The fuel pressurizeed by compression chamber 11 is flowed into dump valve 8 from arrow A1 directions.Cause
This, Z-direction is also the fuel inflow direction from compression chamber 11.
Valve body 8b and valve housing 8d is cylindrical shape.As shown in Fig. 2 on valve housing 8d, 2 taps 803A, 803B exist
Portions 8a side is formed opposite to each other.The fuel discharged from tap 803A, 803B is in arrow A2 directions from the discharge of pump case 1
Mouth 13 flows out, and is supplied to common rail 23 shown in Fig. 1.Moreover, tap can also be set more than at 3 in the circumferential.Valve housing 8d's
Periphery, forms the guiding side face 8d1 formed as shown in Figure 3 from central portion towards right direction, is oriented to side face as shown in Figure 2
A part be cut into plane cutting planes portion 8d2 and form flange part 8d3 in the left side of diagram.On the other hand, exist
The circumference end difference 1a that the inner peripheral surface formation valve housing 8d of pump case 1 flange part 8d3 is abutted.Valve housing 8d by from diagram left direction
The inside of pump case 1 is pressed into, circumference end difference 1a is connected to by valve housing 8d flange part 8d3 and positioned.
Balancing orifice 8d4 is formed in valve housing 8d its right end face.Balancing orifice 8d4 is to enter for making to be discharged to spring 8c
The hole of the fluid turnover in the space of the valve body 8b entered rear side.So, dump valve 8 can in cylinder with the pressure in high press fit pipe
Successfully acted by differential pressure in the presence of power difference.
In addition, in valve housing 8d inner circumferential, forming cylindric guide part 8d5.On guide part 8d5 right side, rank is formed
Terraced portion 8d6.
In valve housing 8d inside, the space for configuring discharge valve spring 8c is formed.It is inserted into discharge valve spring 8c
To after valve housing 8d inside, valve body 8b is inserted.Moved in the valve body 8b elastic forces for revolting discharge valve spring 8c towards right direction
Occasion, discharge valve spring 8c right-hand end is connected to end difference 8d6, prevents valve body 8b movement.That is, end difference 8d6 makees
Worked for the block 805 that has been illustrated in Figure 1.Valve body 8b is guided by guide part 8d5, can be moved back and forth in Z-direction.
The gap of very little is provided between valve body 8b periphery and guide part 8d5, so that valve body 8b can be slided.Therefore, valve body 8b is main in Z
Direction of principal axis is moved back and forth, but at the same time can be moved in direction orthogonal to Z-axis.Therefore, if valve body 8b is relative to guide part
8d5 is offset, then there is the danger for occurring flutter.
Valve body 8b left end face (face faced with portions 8a) is plane, and forms recess 8b1 in the central portion.It is recessed
It is the plane of ring-type around portion 8b1, as valve seat 8b2.
In addition, in the inner peripheral surface of pump case 1, forming the end difference 1b that valve seat member 8A flange part 8A1 is abutted.Valve seat member
8A is pressed into the inside of pump case 1 from the left direction of diagram, valve seat member 8A flange part 8A1 be connected to circumference end difference 1b and
Positioning.Valve seat member 8A inside is hollow shape, and the fuel pressurizeed by compression chamber 11 is flowed into the inside of dump valve 8.Valve seat
Component 8A its right end face is the plane of ring-type, is worked as portions 8a.Valve seat 8b2 and portions 9a are opposite, as both are adjacent to,
Then dump valve 8 is closed, such as both separation, then dump valve 8 is opened.
Valve body 8b valve seat 8b2 surface is parallel to axial direction (the reciprocating directions of valve body 8b with valve body 8b：Z axis side
To) orthogonal plane, in addition, the surface for the portions 8a that valve seat 8b2 is abutted is also parallel with the plane orthogonal with the axial direction of valve body, this
The valve of embodiment is flap type.
Below, the composition of the feature of the dump valve 8 of present embodiment is illustrated.
On valve body 8b valve seat 8b2 periphery, tapering 801 is provided with.Therefore, valve body 8b external diameter is valve housing 8d quilt
The external diameter Rb1 that the diameter Rb2 for the part being inserted into guide part 806 is made than valve seat 8b2 is big.By so constituting, in valve body
Annular interstice is formed between 8b periphery and valve housing 8d inner circumferential.The annular interstice is explained below using Fig. 4.
In addition, the periphery in valve seat member 8A portions 8a sides, forms end difference 8A2.Therefore, valve seat member 8A portions
The external diameter Ra2 in left sides of the external diameter Ra1 than valve seat member 8A of the periphery of 8a sides is smaller.In addition, valve seat member 8A portions 8a sides
Convex portion be located at valve casing 8d inner circumferential side.In addition, the external diameter Ra1 of the periphery of valve seat member 8A portions 8a sides is made than valve casing 8d
Internal diameter 8d1 it is smaller.By so constituting, annular interstice is formed between valve seat member 8A periphery and valve casing 8d inner circumferential.
The annular interstice is explained below using Fig. 4.
Below, illustrated using Fig. 4 and Fig. 5 between the tubulose of the dump valve of the high-pressure fuel feed pump of present embodiment
Gap.
Fig. 4 wants portion to put for expression for the composition of the dump valve of the high-pressure fuel feed pump of first embodiment of the present invention
Big sectional view.In Fig. 4, same section is represented with Fig. 1~Fig. 3 identical symbols.Fig. 5 is for first embodiment of the present invention
High-pressure fuel feed pump dump valve in fuel flowing explanation figure.
As shown in figure 4, forming annular interstice 805B between valve body 8b periphery and valve housing 8d inner circumferential.In addition,
Annular interstice 805C is formed between valve seat member 8A periphery and valve casing 8d inner circumferential.In addition, the state opened in dump valve
Under, there is gap between portions 8a and valve seat 8b2, so, form annular interstice 805A corresponding with the gap.
These annular interstices 805A, 805B, 805C are interconnected.Herein, the sectional area and pipe of conventional annular interstice
Shape gap 805A sectional area is suitable.In contrast, the sectional area of the annular interstice of present embodiment is annular interstice 805A's
The sectional area that the sectional area of sectional area, annular interstice 805B sectional area and annular interstice 805C is added and obtained, thus it is possible to
It is enough big than ever.That is annular interstice 805A, 805B, 805C constitutes liquid damper chamber.Herein, sectional area is as illustrated use
The plane of axle (Z axis in figure) comprising valve body 8b, is area when obtaining the section of dump valve 8.
As shown in figure 5, from axially valve body 8b The fuel stream A1 is crashed into the radial direction of valve body to radiate during dump valve valve opening
Shape disperses.Wherein, as shown in fig. 5 a, foring The fuel stream A2, A3 of tap 803A, 803B scope turns into direct stream
Toward the The fuel stream of tap 803A, 803B valve body radial direction.On the other hand, as shown in Figure 5 B, flow to do not formed tap 803A,
The The fuel stream A4 of 803B scope is circumferential as the valve body for flowing to tap 803A, 803B after valve casing 8d inwall is crashed into
The fuel stream A5, A6.
Herein, crashed into after valve casing 8d inwall shown in Fig. 5 B, flowed to tap 803A, 803B valve body circumference
The fuel stream A5, A6 flows to tap 803A, 803B via the liquid damper chamber illustrated in Fig. 4.As a result, even in valve body 8b
Around pressure distribution produce deviation, its pressure distribution can also relax by liquid damper chamber.
As will be formed in the Z-direction of the annular interstice 805C between valve seat member 8A periphery and valve casing 8d inner circumferential
Length is set to z3, and width is set into x1, then annular interstice 805C sectional area turns into x1z3.In addition, such as setting valve body 8b cone
The length in portion 801 is set to z2, and the width at the top of cone is set into x1, then annular interstice 805B sectional area turn into (x1x2)/
2.In addition, valve body 8b stroke such as is set into ST1, then it is equal with annular interstice 805A length z2.Such as set annular interstice
805A length is set to z1, and width is set into x, then annular interstice 805A sectional area turns into z1x1.
Herein, make annular interstice 805C sectional area of the sectional area than annular interstice 805B big.Concrete example is enumerated, if x1
=0.8mm, z1=0.4mm, z2=1.7mm, z3=2.3mm, then annular interstice 805C sectional area (1.8mm2) than between tubulose
Gap 805B sectional area (0.68mm2) big more than 2 times.
Because, increase the area in tapering 801 such as in order to increase annular interstice 805B area, then annular interstice
Pressure fluctuation in 805B acts on valve body 8b compression area increase, so, it is unfavorable from the viewpoint of Flutter Suppression.Separately
Outside, as valve body 8b is offset in the direction orthogonal with the glide direction of valve body, then also annular interstice 805B sectional area itself sometimes
Change, diminish, be used as the function reduction of liquid buffer.
So, by increasing annular interstice 805C, these problems are can solve the problem that, fully increase the section of liquid damper chamber
Product, can ease off the pressure pulsation.
In the above example, annular interstice 805A sectional area is 0.36mm2, so, the sectional area of liquid damper chamber into
For 2.84mm2.Herein, when for capacity 1500cc, the idling flow of the engine of four cylinders, in order that the pressure loss is rule
, it is necessary to make the sectional area of liquid damper chamber in 0.3mm below definite value2More than.So, only it is annular interstice 805A and by tapering
The sectional area of the 801 annular interstice 805B formed occasion is 1.04mm2, so, to mitigating pressure fluctuation during idling flow
Enough, but for the fuel flow rate of the busy hour of engine, the sectional area just seems inadequate.In contrast,
By plus annular interstice 805C, also can fully it be eased off the pressure arteries and veins for the fuel flow rate of the busy hour of engine
It is dynamic.
Moreover, as the method for forming annular interstice 805B, in addition to setting tapering 801 in valve body 8b, also may be used
Embodiment as be described hereinafter takes the method for setting end difference in valve body 8b like that.But, in the occasion of end difference, pass through portions
8a, the The fuel stream for flowing to tap 803 there is a possibility that occur cavitation as expansion stream drastically.In addition, in end difference
Occasion, the direction of flowing also sharp changes, so, loss in head is also big, produces undesirable pressure fluctuation, also exists and encourages
The possibility of flutter.
In contrast, by setting tapering 801 in valve body 8b as described above, annular interstice 805B is formed, meanwhile, it is capable to
Reduce the direction change of the discharge stream flowed from portions 8a towards tap 803.So, flowing becomes steady, can suppress not wish
The generation of the vortex, cavitation of prestige.
In addition, herein, the aperture area β when sectional area α of fluid passage is relative to dump valve standard-sized sheet turns into α ＞ 0.1
×β.Herein, it is to make that the sectional area α of fluid passage, which refers in the idling flow of the engine of capacity 1500cc four cylinders,
Crushing is in the sectional area (0.3mm2) of the liquid damper chamber below setting.In addition, aperture area β during dump valve standard-sized sheet refers to
Flow to the sectional area that the The fuel stream of tap passes through.That is, aperture area β is the (gap length of valve seat and portions during valve opening
(Fig. 4 ST1=0.4mm)) × (length (3.75mm) × 2 (tap of the part opposite with tap in the periphery of valve seat
Occasion for 2), as 3mm2.Therefore, the sectional area α of fluid passage relative to dump valve standard-sized sheet when aperture area β into
For 0.1 × β of α ＞.
Below, the measurement result of the discharge pressure of the high-pressure fuel feed pump of present embodiment is illustrated using Fig. 6.
Fig. 6 is the explanation figure of the measurement result of the discharge pressure of the high-pressure fuel feed pump of first embodiment of the present invention.
Fig. 6 A represent changes of the pressure P relative to time t of outlet.The pressure P1 represented with fine line represents conventional
The pressure change of outlet in the high-pressure fuel feed pump of composition.Herein, conventional composition refers to does not have in being constituted shown in Fig. 4
There are annular interstice 805B and annular interstice 805C occasion.
On the other hand, the pressure P2 represented with heavy line represents the high compression ignition of the present embodiment illustrated with Fig. 1~Fig. 4
Expect the pressure change of the outlet in supply pump.The high-pressure fuel feed pump of present embodiment be shown in Fig. 4 constitute in except
Also there is annular interstice 805B and annular interstice 805C occasion outside annular interstice 805A.
As shown in Figure 6A, in the embodiment, the pressure oscillation of outlet can be reduced.
Changes of Fig. 6 B to pressure shown in Fig. 6 A carries out Fourier transformation, the pulse amplitude V of outlet pressure is obtained, by horizontal stroke
Axle is expressed as frequency f.The pulse amplitude V1 represented with fine line is the occasion of conventional composition, and the pulsation represented with heavy line is shaken
Width V2 is the occasion of present embodiment.The range of audibility behaved in figure from frequency f1 to frequency f2 scope.So, particularly pair
There is effect in the mitigation of the pulse amplitude of the range of audibility, can mitigate noise.
Below, the assembling procedure of the dump valve 8 of present embodiment is illustrated using Fig. 2.
Seat component 8A, valve body 8b, discharge valve spring 8c and the valve body for the portions 8a that dump valve 8 is illustrated in Fig. 2
Shell 8d is constituted.These parts are arranged on the inside of pump case 1.
Assemble and carried out from the left of pump case 1 shown in Fig. 2.As shown in figure 1, installing electromagnetic suction valve machine in the inside of pump case 1
Structure 30, plunger 2 of compression chamber 11 etc..In the state of before these parts are mounted, pump case 1, which is provided with, to be used to load electromagnetism suction
The hole of valve system 30.Each part of dump valve 8 is inserted from the hole, via the inner space of compression chamber 11, in pump case shown in Fig. 2
Dump valve 8 is assembled in the inner space on 1 right side.
First, valve housing 8d is pressed into and the inner space on right side fixed to pump case 1 shown in Fig. 2 in.Now, valve housing
8d is pressed into the inside of pump case 1 from the left direction of diagram, and valve housing 8d flange part 8d3 abuts to circumference end difference 1a, so that
Positioning.
Then, discharge valve spring 8c is inserted into valve housing 8d inside.
Then, valve body 8b is inserted into valve housing 8d inside.
Finally, seat component 8A is pressed into the inside of pump case 1, valve seat member 8A flange part 8A1 from the left direction of diagram
Circumference end difference 1b is abutted to, so as to position.
In the above description, each part of dump valve 8 fills successively from Fig. 2 left direction from the direction of compression chamber 11
Enter, but also load sometimes from Fig. 2 right direction.Now, it is upwardly formed in the right of pump case 1 and is inserted into a component 8A hole.
From the pore pressure enter with fixed seat component 8A, then, be sequentially inserted into valve body 8b and discharge valve spring 8c, finally, press-in and standing valve
Body shell 8d.
Below, the release valve unit of the dump valve of the high-pressure fuel feed pump as present embodiment is illustrated using Fig. 7
Constitute.
Fig. 7 is the release valve unit of the dump valve of high-pressure fuel feed pump of the expression as first embodiment of the present invention
The sectional view of composition.In Fig. 7 A and Fig. 7 B, if the moving direction of valve is Z axis, axle orthogonal to Z-axis is respectively X-axis, Y-axis.Figure
7A is the longitudinal section on Z-Y plane, and Fig. 7 B are the longitudinal section in Z-X planes.In addition, Fig. 7 A and Fig. 7 B represent dump valve
Valve opening state.In Fig. 7 A and 7B, same section is represented with Fig. 1 identical symbols.
After spring 8c and valve seat 8b are inserted into valve casing 8d inner side, seat portion 8a end difference 8A3 is pressed into valve
Shell 8d inner peripheral surface, so, release valve unit 8 are integrally formed.
As shown in Figure 2, the discharge that can be integratedly constituted from the direction of the compression chamber 11 of Fig. 2 left direction by more than
Valve cell 8U is pressed into the inside of pump case 1, to constitute dump valve.In addition it is possible to by from the right of pump unit 1 shown in Fig. 2
Dump valve is constituted to release valve unit 8U integratedly is pressed into the inside of pump case 1.
As described above, in the embodiment, it can make to crash into valve body from axial direction and with radial disperse
The fuel stream in, The fuel stream that flow to the scope for not forming tap led to by forming the fluid of circumferential liquid damper chamber
Road, actively and is evenly guided towards tap.As a result, it is possible to eliminate deviation in the pressure distribution around valve body, mitigate and make
For the differential pressure of valve body, suppress flutter.
In addition, even in valve body from the center of valve housing toward radial deflection in the case of, also can be by being pre-formed
Circumferential fluid passage (tubular conduit 805C) with sectional area more than setting, by the sectional area rate of change before and after skew
It is kept as smaller, as a result, the differential pressure for resulting from valve body both sides can be reduced, suppresses flutter.
In addition, forming a part for fluid passage by the surface of the component beyond valve body, it is not required to make in fluid passage
Pressure fluctuation act on valve body compression area increase just the sectional area of fluid passage can be made increase, play towards circumference it is abundant
Fluid guiding function, and there occurs in fluid passage pressure fluctuation, the shadow that will can be also produced to valve body movement
Ring and be suppressed to Min., suppress flutter.
That is, by the pressure fluctuation of the sensitive high frequency field of the ear that mitigates people, it can avoid or suppress outward appearance shape
The maximizing of shape, the complication of the layout of high press fit pipe and the cost increase thus brought etc., and be greatly reduced with
The noise that high pressure, big flowization are produced.
As described above, the influence of the noise as caused by valve body circumferential The fuel stream can be mitigated.
In the above description, the valve body and valve housing of tubular have been used, but the valve of the shape beyond this passes through with same
Method circumferentially formed fluid passage, can also suppress the flutter of valve body.
Below, composition and the action of the high-pressure fuel feed pump of second embodiment of the present invention are illustrated using Fig. 8.Use this
The composition of the high pressure fuel supply system of the high-pressure fuel feed pump of embodiment is identical with composition Fig. 1 Suo Shi.
Fig. 8 regards to represent to be used for the vertical profile of the composition of the dump valve of the high-pressure fuel feed pump of second embodiment of the present invention
Figure.Fig. 8 represents the valve opening state of dump valve.In fig. 8, same section is represented with Fig. 1~Fig. 4 identical symbols.
In the present embodiment, dump valve 8 is made up of portions 8a, valve body 8b, discharge valve spring 8c and valve housing 8d.Valve
Body 8b and valve housing 8d is cylindrical shape, and tap 803A, 803B are formed at 2 positions opposite to each other in portions 8a side.Moreover,
Tap can also be set more than at 3 in the circumferential.
In the present embodiment, valve body 8b external diameter is the straight of the valve housing 8d part being inserted into guide part 8d5
The external diameter that footpath is made than portions 8a is big, and end difference 802 is provided with valve body 8b valve seat 8b2 periphery.
By so constituting, annular interstice 805B is formed between valve body 8b and valve housing 8d.In such manner, it is possible to make to crash into
Flowed to after valve body 8b with fuel in radial dispersed The fuel stream, to flow to the scope for not forming tap 803A, 803B
Valve body 8b circumferential revolution, can successfully be guided to nearest tap 803A, 803B.As a result, it can make around valve body 8b
The deviation of pressure distribution is relaxed.
In addition, in the same manner as the 1st embodiment being illustrated in Figure 4 in portions 8a peripheral part and valve housing 8d
Annular interstice 805C is formed between the portion of footpath.In addition to annular interstice 805B, by setting annular interstice 805C, without increasing tubulose
The compression area that pressure fluctuation in gap acts on valve body 8b can ensure that enough sectional areas, can suppress quivering for valve body 8b
Shake, mitigate noise.In addition, sectional area of the annular interstice 805C sectional area than annular interstice 805B is big, can ease off the pressure arteries and veins
The compression area of action.
Constitute, in the present embodiment, can also mitigate as caused by the circumferential The fuel stream of valve body according to described above
The influence of noise.
In the above description, the valve body and valve housing of tubular have been used, but in the valve of shape in addition, according to same
Method circumferentially formed fluid passage, can also suppress the flutter of valve body.
Below, composition and the action of the high-pressure fuel feed pump of the 3rd embodiment of the present invention are illustrated using Fig. 9.Use
The composition of the high pressure fuel supply system of the high-pressure fuel feed pump of present embodiment is identical with composition Fig. 1 Suo Shi.
Fig. 9 regards to represent to be used for the vertical profile of the composition of the dump valve of the high-pressure fuel feed pump of third embodiment of the present invention
Figure.Fig. 9 represents the valve opening state of dump valve.In fig .9, same section is represented with Fig. 1~Fig. 4 identical symbols.
In the present embodiment, using the guide part 806 for being not provided with Fig. 2, Fig. 8 illustrated embodiment tabular valve body
8b.The valve body 8b of tabular is such as used, then relative to the valve body with guide part as the embodiment used shown in Fig. 2, Fig. 8
Situation, structure and handling ease, to reduction cost advantages.However, there occurs undesirable valve body movement due to being not disposed on
When the mechanism that is suppressed to it, so, from noise mitigate and Reliability of Microprocessor from the viewpoint of must all suppress flutter.
Occasion with the valve body with guide part is same, and the external diameter that valve body 8b external diameter is made than portions 8a is big, provided with tapering
807.So, annular interstice 805B is formed, stable The fuel stream, the deviation for the distribution that can ease off the pressure can be circumferentially being produced.
In addition, by setting tapering 807, the direction change of the main flow for the radial direction for flowing to tap 803A, 803B can be reduced, put down it
Steadyization.
Constituted according to described above, in the present embodiment, can mitigate and be made an uproar as caused by the circumferential The fuel stream of valve body
The influence of sound.
The invention is not restricted to the high-pressure fuel feed pump of internal combustion engine, various supply pumps can be widely used for.
Claims (8)
1. a kind of high-pressure fuel feed pump, possesses the row in the compression chamber pressurizeed to fluid and the downstream located at above-mentioned compression chamber
Go out valve, it is characterised in that：
The dump valve possesses：
Valve housing, is formed as tubular；
Valve body, is maintained at the inside of above-mentioned valve housing in the way of it can slide；
Valve seat member, is partly housed in the inside of above-mentioned valve housing, and with being abutted with above-mentioned valve body and close valve
Portions；And
Valve spring is discharged, above-mentioned valve body is exerted a force to above-mentioned portions,
On above-mentioned valve housing, circumferentially arranged with multiple taps, above-mentioned multiple taps, which turn into, makes above-mentioned fluid from the valve body
The inner circumferential side of the shell path that radially the week side of boss circulates,
Between the inner peripheral surface of above-mentioned valve housing in the scope for not forming above-mentioned tap and the outer peripheral face of above-mentioned valve seat member,
It is formed with and is connected and turns into the tubular passageway for the path for making above-mentioned fluid circumferentially circulate with above-mentioned tap.
2. high-pressure fuel feed pump according to claim 1, it is characterised in that：
Be formed with end difference in the outer peripheral face of above-mentioned valve seat member, the end difference have abutted with above-mentioned valve housing the 1st region,
The 2nd small region with above-mentioned 1st region of external diameter ratio,
The formation of above described tubular path is between above-mentioned valve housing and above-mentioned 2nd region.
3. high-pressure fuel feed pump according to claim 1, it is characterised in that：
When the outer peripheral face of above-mentioned valve body is formed with the peripheral part of the inner peripheral surface sliding contact of above-mentioned valve housing, in valve closing with it is upper
The tapering stated the seat portion of portions abutting and formed between above-mentioned peripheral part and above-mentioned seat portion,
Above described tubular path is connected with the annular interstice between the inner peripheral surface of above-mentioned valve housing and the above-mentioned tapering of above-mentioned valve body.
4. high-pressure fuel feed pump according to claim 1, it is characterised in that：
When the outer peripheral face of above-mentioned valve body is formed with the peripheral part of the inner peripheral surface sliding contact of above-mentioned valve housing, in valve closing with it is upper
The end difference stated the seat portion of portions abutting and formed between above-mentioned peripheral part and above-mentioned seat portion,
Above described tubular path is connected with the annular interstice between the inner peripheral surface of above-mentioned valve housing and the above-mentioned end difference of above-mentioned valve body.
5. the high-pressure fuel feed pump according to claim 3 or 4, it is characterised in that：
Include the sectional area of the above described tubular path in the plane including the axle of above-mentioned valve body, than the sectional area in above described tubular gap
Greatly.
6. high-pressure fuel feed pump according to claim 1, it is characterised in that：
Above-mentioned valve body has the recessed of the internal side diameter of the seat portion abutted in valve closing with above-mentioned portions and formation in above-mentioned seat portion
Portion.
7. high-pressure fuel feed pump according to claim 1, it is characterised in that：
The block limited the path increment of above-mentioned valve body is formed with above-mentioned valve housing.
8. a kind of release valve unit,
The release valve unit possesses：
Valve housing, is formed as tubular；
Valve body, is maintained at the inside of above-mentioned valve housing in the way of it can slide；
Valve seat member, is partly housed in the inside of above-mentioned valve housing, and with being abutted with above-mentioned valve body and close valve
Portions；And
Valve spring is discharged, above-mentioned valve body is exerted a force to above-mentioned portions,
It is characterized in that：
On above-mentioned valve housing, circumferentially arranged with multiple taps, above-mentioned multiple taps, which turn into, makes fluid from the valve housing
The inner circumferential side path that radially the week side of boss circulates,
Between the inner peripheral surface of above-mentioned valve housing in the scope for not forming above-mentioned tap and the outer peripheral face of above-mentioned valve seat member,
It is formed with and is connected and turns into the tubular passageway for the path for making above-mentioned fluid circumferentially circulate with above-mentioned tap.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510088756.0A CN104775957B (en) | 2009-02-20 | 2009-02-20 | High-pressure fuel feed pump and the release valve unit for the pump |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200980156950.0A CN102325987B (en) | 2009-02-20 | 2009-02-20 | High-pressure fuel feed pump, and discharge valve unit used therein |
| CN201510088756.0A CN104775957B (en) | 2009-02-20 | 2009-02-20 | High-pressure fuel feed pump and the release valve unit for the pump |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200980156950.0A Division CN102325987B (en) | 2009-02-20 | 2009-02-20 | High-pressure fuel feed pump, and discharge valve unit used therein |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104775957A CN104775957A (en) | 2015-07-15 |
| CN104775957B true CN104775957B (en) | 2017-10-17 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510088756.0A Active CN104775957B (en) | 2009-02-20 | 2009-02-20 | High-pressure fuel feed pump and the release valve unit for the pump |
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| Country | Link |
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| CN (1) | CN104775957B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6800593B2 (en) * | 2016-03-18 | 2020-12-16 | 日立オートモティブシステムズ株式会社 | Pump device |
| US11002236B2 (en) * | 2016-11-18 | 2021-05-11 | Hitachi Automotive Systems, Ltd. | High-pressure fuel supply pump |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0522969U (en) * | 1990-12-25 | 1993-03-26 | 株式会社アツギユニシア | Check valve |
| JPH0566275U (en) * | 1992-02-12 | 1993-09-03 | 株式会社ユニシアジェックス | Check valve mechanism of plunger pump |
| CN1413290A (en) * | 2000-08-24 | 2003-04-23 | 三菱电机株式会社 | Solenoid valve for variable discharge fuel supply apparatus |
| CN1809694A (en) * | 2003-06-17 | 2006-07-26 | 瓦特西拉芬兰有限公司 | Arrangement in fuel injection apparatus |
| JP2006207451A (en) * | 2005-01-27 | 2006-08-10 | Toyota Motor Corp | Fuel pump and delivery valve equipped in fuel pump |
-
2009
- 2009-02-20 CN CN201510088756.0A patent/CN104775957B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0522969U (en) * | 1990-12-25 | 1993-03-26 | 株式会社アツギユニシア | Check valve |
| JPH0566275U (en) * | 1992-02-12 | 1993-09-03 | 株式会社ユニシアジェックス | Check valve mechanism of plunger pump |
| CN1413290A (en) * | 2000-08-24 | 2003-04-23 | 三菱电机株式会社 | Solenoid valve for variable discharge fuel supply apparatus |
| CN1809694A (en) * | 2003-06-17 | 2006-07-26 | 瓦特西拉芬兰有限公司 | Arrangement in fuel injection apparatus |
| JP2006207451A (en) * | 2005-01-27 | 2006-08-10 | Toyota Motor Corp | Fuel pump and delivery valve equipped in fuel pump |
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| CN104775957A (en) | 2015-07-15 |
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