Source: https://patents.google.com/patent/JP5180365B2/en
Timestamp: 2020-04-04 22:51:26
Document Index: 73161625

Matched Legal Cases: ['art 2', 'art 8', 'art 8', 'art 8', 'art 8', 'art 8', 'art 8', 'art 9']

JP5180365B2 - High pressure fuel supply pump and discharge valve unit used therefor - Google Patents
High pressure fuel supply pump and discharge valve unit used therefor Download PDF
JP5180365B2
JP5180365B2 JP2011500416A JP2011500416A JP5180365B2 JP 5180365 B2 JP5180365 B2 JP 5180365B2 JP 2011500416 A JP2011500416 A JP 2011500416A JP 2011500416 A JP2011500416 A JP 2011500416A JP 5180365 B2 JP5180365 B2 JP 5180365B2
JP2011500416A
JPWO2010095247A1 (en
俊亮 有冨
英紀 町村
雅巳 阿部
健一郎 徳尾
2009-02-20 Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
2009-02-20 Priority to PCT/JP2009/053077 priority Critical patent/WO2010095247A1/en
2012-08-16 Publication of JPWO2010095247A1 publication Critical patent/JPWO2010095247A1/en
2013-04-10 Publication of JP5180365B2 publication Critical patent/JP5180365B2/en
The present invention relates to a high-pressure fuel supply pump for supplying fuel to an engine at a high pressure and a discharge valve unit used therefor, and more particularly to a high-pressure fuel supply pump suitable for preventing fluttering of the discharge valve and a discharge valve unit used therefor.
In general, in a device for pressurizing a fluid, various noises such as a collision sound and a pressure pulsation sound are generated due to the pressurizing operation. In response to this, measures have been taken to absorb the generated pressure pulsation with a hydraulic damper such as an accumulator, or to absorb the generated noise with a sound insulation material. It is disadvantageous from the viewpoint of cost.
Therefore, a valve structure in which a noise reduction function is provided in the valve unit has been studied.
For example, firstly, in a check valve configured to discharge fuel in a radial direction from a plurality of discharge ports formed in a valve housing, a valve structure provided with a buffer portion for buffering the pressure of hydraulic fluid after passing through the discharge port is known. (For example, refer to Patent Document 1).
Secondly, in the check valve, the valve seat is formed in a tapered shape so that the direction change of the discharge flow flowing from the valve seat to the discharge port is small and flows smoothly, and a conical portion seated on the valve seat is provided in the valve body. A known valve structure is known (see, for example, Patent Document 2).
Japanese Utility Model Publication No. 5-66275 Japanese Utility Model Publication No. 5-22969
In the valve having the configuration described in Patent Document 1 or Patent Document 2, the flow that collides with the valve body from the axial direction when the valve is opened is radially dispersed in the radial direction of the valve body. Among these, the flow in the range where the discharge port is formed becomes the flow in the radial direction of the valve body as it is toward the discharge port. On the other hand, the flow toward the range where the discharge port is not formed becomes a flow in the circumferential direction of the valve body toward the discharge port after colliding with the inner wall of the valve housing.
In the valves described in Patent Document 1 and Patent Document 2, the flow toward the area where the discharge port is not formed is not a high-pressure / high-speed flow in the circumferential direction of the valve body, and the influence on the valve body behavior is negligible. First, a behavior that causes pressure pulsation (hereinafter referred to as fluttering) is excited.
In general, a ball valve using a spherical valve body can obtain a relatively large flow rate even if the valve body moves in a small axial direction. The relationship becomes non-linear. On the other hand, in the flat valve, the relationship between the axial movement amount of the valve body and the discharge amount is a straight line. Here, the flat valve is such that the surface of the valve seat of the valve body is parallel to a plane perpendicular to the axial direction of the valve body, and the surface of the seat portion with which the valve body abuts is also in the axial direction of the valve body. It is parallel to an orthogonal plane. The valve described in Patent Document 1 is a flat valve. However, in the flat valve, in order to discharge a large flow rate, it is necessary to increase the amount of movement of the valve body in the axial direction. There is a gap between the valve body housing that slides and holds the valve body, and the cross-sectional area through which the circumferential flow passes on both sides of the valve body when the valve body is radially offset from the center of the valve body housing Makes a big difference. As a result, the differential pressure acting on the valve body increases, and fluttering occurs using this as an exciting force. Fluttering is more likely to occur as the amount of movement of the valve body in the axial direction increases, and a flat valve that discharges a large flow rate tends to cause a problem.
Fluttering is a vibration in a direction perpendicular to the opening / closing valve operating direction of the valve body. When this occurs, fuel around the valve body is affected and pressure pulsation occurs. The pressure pulsation generated in this way is propagated and amplified through the piping system and is emitted to the outside as noise, which causes noise.
An object of the present invention is to provide a high-pressure fuel supply pump equipped with a discharge valve that can reduce the influence of noise caused by the flow in the circumferential direction of the valve body, and a discharge valve unit used therefor.
(1) In order to achieve the above object, the present invention provides a pressurizing chamber whose volume is changed by a reciprocating motion of a plunger, a discharge port for discharging fuel pressurized by the pressurizing chamber, A discharge valve that is provided between the pressurizing chambers and is a check valve, the discharge valve having a plurality of discharge ports that communicate with the discharge port, and the valve body housing A valve body that is biased in a direction to close the valve by a discharge valve spring, and a seat portion that is housed in the valve body housing and closes the valve in contact with the valve body. A high-pressure fuel supply pump comprising a seat member having a valve seat surface formed on the valve body and a surface of the seat portion parallel to a plane perpendicular to the axial direction of the valve body. Is a flat valve, and when the valve is opened, The flow of fuel colliding with the valve body from the axial direction through the hollow portion of the seat member is radially dispersed in the radial direction of the valve body, and collides with the flow directly toward the discharge port and the inner wall of the valve housing. After that, the flow of the valve body toward the discharge port flows in the circumferential direction, and is formed between the outer periphery of the seat member and the outer periphery of the valve body and the inner periphery of the valve housing. The liquid damper chamber includes a first tubular passage formed between an outer periphery of the valve body and an inner periphery of the valve housing, and an interval between the outer periphery of the seat member and the inner periphery of the valve housing. is obtained by the so that a second tubular passage formed in the.
With such a configuration, the influence of noise caused by the flow in the circumferential direction of the valve body can be reduced.
( 2 ) In the above ( 1 ), preferably, the first and second tubular passages have a cross-sectional area of the second tubular passage in a plane including the axis of the valve body, the cross-sectional area of the first tubular passage being It is larger than the cross-sectional area.
( 3 ) In the above ( 2 ), preferably, the outer diameter of the valve body is larger than the outer diameter of the valve seat.
( 4 ) In the above ( 3 ), preferably, the first tubular passage is formed between a taper provided on an outer periphery of the valve seat of the valve body and an inner periphery of the valve housing. is there.
( 5 ) In the above (1), preferably, the liquid damper chamber has a cross-sectional area larger than 0.3 mm 2 in a plane including the axis of the valve body.
( 6 ) Moreover, in order to achieve the said objective, this invention is used for the high pressure fuel supply pump which discharges the fuel pressurized by the pressurization chamber from the discharge outlet through the discharge valve which is a check valve, A discharge valve unit that is press-fitted into a valve body housing constituting a part of the discharge valve, wherein the discharge valve unit is biased in a direction to close the valve by a discharge valve spring, and the valve body The discharge valve includes a seat member having a seat portion that closes the valve, and the surface of the valve seat formed on the valve body and the surface of the seat portion are orthogonal to the axial direction of the valve body. A flat valve that is parallel to a plane, and when the valve is opened, the flow of fuel that has collided with the valve body from the axial direction through the hollow portion of the seat member is radial in the radial direction of the valve body. Flow to the discharge port and the valve housing After colliding with the inner wall of the valve, it flows toward the discharge port in the circumferential direction of the valve body, and is formed between the outer periphery of the seat member and the outer periphery of the valve body and the inner periphery of the valve housing. A liquid damper chamber for flow, wherein the liquid damper chamber includes a first tubular passage formed between an outer periphery of the valve body and an inner periphery of the valve housing, an outer periphery of the seat member, and the valve housing. And a second tubular passage formed between the inner periphery and the inner periphery.
According to the present invention, the influence of noise caused by the flow in the circumferential direction of the valve body can be reduced.
Hereinafter, the configuration and operation of the high-pressure fuel supply pump according to the first embodiment of the present invention will be described with reference to FIGS.
First, the configuration of a high-pressure fuel supply system using the high-pressure fuel supply pump according to the present embodiment will be described with reference to FIG.
FIG. 1 is an overall configuration diagram of a high-pressure fuel supply system using a high-pressure fuel supply pump according to a first embodiment of the present invention.
In FIG. A portion surrounded by a broken line indicates a pump housing 1 of the high pressure fuel supply pump, and a mechanism and parts shown in the broken line are integrally incorporated therein to constitute the high pressure fuel supply pump of the present embodiment. doing. Moreover, in the figure, the dotted line has shown the flow of the electrical signal.
The fuel in the fuel tank 20 is pumped up by the feed pump 21 and sent to the fuel inlet 10 a of the pump housing 1 through the suction pipe 28. The fuel that has passed through the fuel suction port 10a reaches the suction port 30a of the electromagnetic suction valve mechanism 30 constituting the variable capacity mechanism via the pressure pulsation reducing mechanism 9 and the suction passage 10c.
The electromagnetic intake valve mechanism 30 includes an electromagnetic coil 30b. With the electromagnetic coil 30b energized, the electromagnetic plunger 30c compresses the spring 33 and moves to the right in FIG. 1, and this state is maintained. At this time, the suction valve body 31 attached to the tip of the electromagnetic plunger 30c opens the suction port 32 leading to the pressurizing chamber 11 of the high pressure fuel supply pump. When the electromagnetic coil 30 b is not energized and there is no fluid differential pressure between the suction passage 10 c (suction port 30 a) and the pressurizing chamber 11, the suction valve body 31 is moved by the biasing force of the spring 33. The suction port 32 is urged in the valve closing direction (leftward in FIG. 3) to be closed, and this state is maintained. FIG. 1 shows a state where the suction port 32 is closed.
A plunger 2 is held in the pressurizing chamber 11 so as to be slidable in the vertical direction of FIG. When the plunger 2 is displaced downward in FIG. 1 due to the rotation of the cam of the internal combustion engine and is in the suction process state, the volume of the pressurizing chamber 11 increases and the fuel pressure therein decreases. In this step, when the fuel pressure in the pressurizing chamber 11 becomes lower than the pressure in the suction passage 10c (suction port 30a), the suction valve body 31 has a valve opening force (suction valve body 31 shown in FIG. 1) is generated. By this valve opening force, the suction valve body 31 overcomes the urging force of the spring 33 and opens to open the suction port 32. In this state, when a control signal from the ECU 27 is applied to the electromagnetic intake valve mechanism 30, a current flows through the electromagnetic coil 30b of the electromagnetic intake valve 30, and the electromagnetic plunger 30c moves to the right in FIG. Then, the state where the suction port 32 is opened is maintained.
When the plunger 2 shifts from the suction process to the compression process (the ascending process from the lower start point to the upper start point) while maintaining the application state of the input voltage to the electromagnetic intake valve mechanism 30, the energized state of the electromagnetic coil 30b is changed. Since it is maintained, the magnetic urging force is maintained, and the suction valve body 31 still maintains the opened state. The volume of the pressurizing chamber 11 decreases with the compression movement of the plunger 2. In this state, the fuel once sucked into the pressurizing chamber 11 is once again opened into the intake valve body 31 and the inlet 32. Between the pressure chamber 11 and the suction passage 10c (suction port 30a), the pressure in the pressurizing chamber 11 does not increase. This process is called a return process.
In the returning step, when the energization to the electromagnetic coil 30b is cut off, the magnetic urging force acting on the electromagnetic plunger 30c is erased after a certain time (after magnetic and mechanical delay time). Then, the suction valve body 31 moves to the left in FIG. 1 and closes the suction port 32 by the urging force of the spring 33 that is constantly working on the suction valve body 31 and the fluid force generated by the pressure loss of the suction port 32. . When the suction port 32 is closed, the fuel pressure in the pressurizing chamber 11 rises with the rise of the plunger 2 from this time. Then, when the fuel pressure in the pressurizing chamber 11 exceeds a pressure larger than the fuel pressure in the discharge port 13 by a predetermined value, the fuel remaining in the pressurizing chamber 11 passes through the discharge valve 8 and becomes a high pressure. Discharge is performed and supplied to the common rail 23. This process is called a discharge process. As described above, the compression process of the plunger 2 includes a return process and a discharge process.
During the returning process, a pressure pulsation is generated in the suction passage due to the fuel returned to the suction passage 10c. Most of the energy is absorbed by the pressure pulsation reducing mechanism 9.
The ECU 27 can control the amount of high-pressure fuel to be discharged by controlling the timing of releasing energization of the electromagnetic coil 30 c of the electromagnetic intake valve mechanism 30. If the timing of releasing the energization to the electromagnetic coil 30b is advanced, the ratio of the return process in the compression process is reduced and the ratio of the discharge process is increased. That is, the amount of fuel returned to the suction passage 10c (suction port 30a) is reduced and the amount of fuel discharged at high pressure is increased. On the other hand, if the timing of releasing the energization is delayed, the ratio of the return process in the compression process is increased and the ratio of the discharge process is decreased. That is, more fuel is returned to the suction passage 10c and less fuel is discharged at high pressure. The timing for releasing the energization is controlled by a command from the ECU 27.
As described above, the ECU 27 controls the timing of releasing the energization of the electromagnetic coil, whereby the amount of fuel discharged at high pressure can be set to an amount required by the internal combustion engine.
In the pump housing 1, a discharge valve 8 is provided on the outlet side of the pressurizing chamber 11 between the discharge port (discharge side pipe connection portion) 13. The discharge valve 8 includes a seat portion 8a, a valve body 8b, a discharge valve spring 8c, and a valve body housing 8d. In a state where there is no fuel differential pressure between the pressurizing chamber 11 and the discharge port 13, the valve body 8b is pressed against the seat portion 8a by the urging force of the discharge valve spring 8c and is in a closed state. When the fuel pressure in the pressurizing chamber 11 exceeds a pressure larger than the fuel pressure in the discharge port 13 by a predetermined value, the valve body 8b opens against the discharge valve spring 8c, and the inside of the pressurizing chamber 11 The fuel is discharged to the discharge port 13 through the discharge valve 8.
After the valve body 8b is opened, the operation is restricted when it comes into contact with a stopper 805 formed on the valve body housing 8d. Therefore, the stroke of the valve body 8b is appropriately determined by the valve body housing 8d. If the stroke is too large, the fuel discharged to the discharge port 13 flows back into the pressurizing chamber 11 again due to the delay in closing the valve body 8b, so that the efficiency of the high-pressure pump decreases. Further, the valve body 8b is guided by the inner wall 806 of the valve body housing 8d so as to smoothly move in the stroke direction when the valve body 8b repeats opening and closing movements. By configuring as described above, the discharge valve 8 becomes a check valve that restricts the flow direction of fuel. The detailed configuration of the discharge valve 8 will be described later with reference to FIGS.
As described above, the fuel guided to the fuel suction port 10a is pressurized to a high pressure by the reciprocating motion of the plunger 2 in the pressurizing chamber 11 of the pump housing 1, and through the discharge valve 8, It is pumped from the discharge port 13 to a common rail 23 that is a high-pressure pipe.
In addition, the example using a normally closed solenoid valve that is closed when no current is supplied and opened when the current is supplied has been described, but conversely, the valve is open when no current is supplied. A normally open type electromagnetic valve that is sometimes closed may be used. In this case, the flow control command from the ECU 27 is reversed between ON and OFF.
An injector 24 and a pressure sensor 26 are attached to the common rail 23. The injectors 24 are mounted according to the number of cylinders of the internal combustion engine, and the injectors 24 are opened and closed by a control signal from the ECU 27 to inject a predetermined amount of fuel into the cylinders.
Next, the configuration of the discharge valve used in the high-pressure fuel supply pump according to the present embodiment will be described with reference to FIGS.
2 and 3 are longitudinal sectional views showing the configuration of the discharge valve used in the high-pressure fuel supply pump according to the first embodiment of the present invention. 2 and 3, the moving direction of the valve is taken as the Z axis, and the axes orthogonal to the Z axis are taken as the X axis and the Y axis, respectively. 2 is a longitudinal sectional view in the ZY plane, and FIG. 3 is a longitudinal sectional view in the ZX plane. 2 and 3 show the opened state of the discharge valve. 2 and 3, the same reference numerals as those in FIG. 1 denote the same parts.
The discharge valve 8 includes the seat portion 8a, the valve body 8b, the discharge valve spring 8c, and the valve body housing 8d described with reference to FIG. The seat portion 8a, the valve body 8b, the discharge valve spring 8c, and the valve body housing 8d are all made of metal. The sheet portion 8a is formed at one end of the sheet member 8A. The valve body housing 8d and the seat member 8A are press-fitted into the metal pump housing 1 and fixed. The valve body 8b is slidably held inside the valve body housing 8d. In the figure, the Z-axis direction is the sliding direction of the valve body 8b. A discharge valve spring 8c is inserted between the valve body 8b and the valve body housing 8d. The discharge valve spring 8c urges the valve body 8b in the direction opposite to the fuel inflow direction. As described with reference to FIG. 1, the pressurizing chamber 11 is provided inside the pump housing 1. The fuel pressurized in the pressurizing chamber 11 flows into the discharge valve 8 from the direction of the arrow A1. Therefore, the Z-axis direction is also the fuel inflow direction from the pressurizing chamber 11.
The valve body 8b and the valve body housing 8d are cylindrical. As shown in FIG. 2, the valve body housing 8d is formed with two discharge ports 803A and 803B facing the side of the seat portion 8a. The fuel discharged from the discharge ports 803A and 803B flows out from the discharge port 13 of the pump housing 1 in the direction of arrow A2, and is supplied to the common rail 23 shown in FIG. Note that three or more discharge ports may be provided in the circumferential direction. On the outer periphery of the valve body housing 8d, as shown in FIG. 3, a guide peripheral surface 8d1 formed in the right direction from the center portion and a guide peripheral surface shown in FIG. A cut flat surface portion 8d2 and a flange portion 8d3 formed on the left side of the figure are formed. On the other hand, a circumferential stepped portion 1a with which the flange portion 8d3 of the valve body housing 8d abuts is formed on the inner peripheral surface of the pump housing 1. The valve body housing 8d is press-fitted into the pump housing 1 from the left side of the figure, and is positioned by the flange portion 8d3 of the valve body housing 8d coming into contact with the circumferential stepped portion 1a.
A pressure equalizing hole 8d4 is formed on the right end surface of the valve body housing 8d. The pressure equalizing hole 8d4 is a hole for the fluid discharged into and out of the space on the back side of the valve body 8b in which the spring 8c is inserted. As a result, the discharge valve 8 can operate smoothly by receiving a differential pressure due to a pressure difference between the cylinder and the high-pressure pipe.
A cylindrical guide portion 8d5 is formed on the inner periphery of the valve body housing 8d. A stepped portion 8d6 is formed on the right side of the guide portion 8d5.
A space for disposing the discharge valve spring 8c is formed inside the valve body housing 8d. After the discharge valve spring 8c is inserted into the valve body housing 8d, the valve body 8b is inserted. When the valve body 8b moves rightward against the urging force of the discharge valve spring 8c, the right end portion of the discharge valve spring 8c comes into contact with the stepped portion 8d6 to prevent the valve body 8b from moving. That is, the stepped portion 8d6 functions as the stopper 805 described with reference to FIG. The valve body 8b is guided by the guide portion 8d5 and can reciprocate in the Z-axis direction. A slight gap is provided between the outer periphery of the valve body 8b and the guide portion 8d5 so that the valve body 8b can slide. Therefore, the valve body 8b reciprocates mainly in the Z-axis direction, but can move in the direction perpendicular to the Z-axis. Therefore, if the valve body 8b is offset with respect to the guide portion 8d5, fluttering may occur.
The left end surface of the valve body 8b (surface facing the seat portion 8a) is a flat surface, and a concave portion 8b1 is formed at the center thereof. The periphery of the recess 8b1 is a ring-shaped plane, which becomes the valve seat 8b2.
Further, a circumferential stepped portion 1b with which the flange portion 8A1 of the valve seat member 8A abuts is formed on the inner peripheral surface of the pump housing 1. The valve seat member 8A is press-fitted into the pump housing 1 from the left direction in the figure, and is positioned by the flange portion 8A1 of the valve seat member 8A coming into contact with the circumferential stepped portion 1b. The inside of the valve seat member 8 </ b> A is hollow, and the fuel pressurized in the pressurizing chamber 11 flows into the discharge valve 8. The right end surface of the valve seat member 8A is a ring-shaped plane and functions as the seat portion 8a. The valve seat 8b2 and the seat portion 9a are opposed to each other, and when the two are in close contact, the discharge valve 8 is closed, and when both are separated, the discharge valve 8 is opened.
The surface of the valve seat 8b2 of the valve body 8b is parallel to a plane orthogonal to the axial direction of the valve body 8b (the direction in which the valve body 8b reciprocates: the Z-axis direction), and the seat portion with which the valve seat 8b2 abuts. The surface of 8a is also parallel to the plane orthogonal to the axial direction of the valve body, and the valve of this embodiment is a flat valve.
Next, a characteristic configuration of the discharge valve 8 of the present embodiment will be described.
A tapered portion 801 is provided around the valve seat 8b2 of the valve body 8b. Therefore, the outer diameter of the valve body 8b, that is, the diameter Rb2 of the portion inserted into the guide portion 806 of the valve body housing 8d is configured to be larger than the outer diameter Rb1 of the valve seat 8b2. With such a configuration, a tubular gap is formed between the outer periphery of the valve body 8b and the inner periphery of the valve body housing 8d. This tubular gap will be described later with reference to FIG.
Further, a stepped portion 8A2 is formed on the outer periphery of the valve seat member 8A on the seat portion 8a side. Therefore, the outer diameter Ra1 of the outer periphery on the seat portion 8a side of the valve seat member 8A is smaller than the outer diameter Ra2 on the left side of the valve seat member 8A. Further, the convex portion on the seat portion 8a side of the valve seat member 8A is located on the inner peripheral side of the valve housing 8d. The outer diameter Ra1 of the outer periphery of the valve seat member 8A on the seat portion 8a side is configured to be smaller than the inner diameter 8d1 of the valve housing 8d. With such a configuration, a tubular gap is formed between the outer periphery of the valve seat member 8A and the inner periphery of the valve housing 8d. This tubular gap will be described later with reference to FIG.
Next, the tubular gap provided in the discharge valve of the high-pressure fuel supply pump according to the present embodiment will be described with reference to FIGS. 4 and 5.
FIG. 4 is an enlarged cross-sectional view of the main part showing the configuration of the discharge valve used in the high-pressure fuel supply pump according to the first embodiment of the present invention. In FIG. 4, the same reference numerals as those in FIGS. 1 to 3 denote the same parts. FIG. 5 is an explanatory diagram of the fuel flow in the discharge valve used in the high-pressure fuel supply pump according to the first embodiment of the present invention.
As shown in FIG. 4, a tubular gap 805B is formed between the outer periphery of the valve body 8b and the inner periphery of the valve body housing 8d. Further, a tubular gap 805C is formed between the outer periphery of the valve seat member 8A and the inner periphery of the valve housing 8d. Furthermore, in a state where the discharge valve is open, there is a gap between the seat portion 8a and the valve seat 8b2, and thus a tubular gap 805A corresponding to this gap is formed.
These tubular gaps 805A, 805B, and 805C communicate with each other. Here, the cross-sectional area of the conventional tubular gap corresponds to the cross-sectional area of the tubular gap 805A. On the other hand, the cross-sectional area of the tubular gap according to the present embodiment is the sum of the cross-sectional area of the tubular gap 805A, the cross-sectional area of the tubular gap 805B, and the cross-sectional area of the tubular gap 805C. That is, the tubular gaps 805A, 805B, and 805C constitute a liquid damper chamber. Here, the cross sectional area is an area when a cross section of the discharge valve 8 is obtained on a plane including the axis of the valve body 8b (Z axis in the drawing) as shown in the figure.
As shown in FIG. 5, the flow A1 colliding with the valve body 8b from the axial direction when the discharge valve is opened is radially dispersed in the radial direction of the valve body. Among these, as shown in FIG. 5A, the flows A2 and A3 in the range where the discharge ports 803A and 803B are formed are directly flowed toward the discharge ports 803A and 803B in the radial direction of the valve body. On the other hand, as shown in FIG. 5B, the flow A4 toward the area where the discharge ports 803A and 803B are not formed collides with the inner wall of the valve housing 8d and then faces the discharge ports 803A and 803B in the circumferential direction of the valve body. It becomes flow A5, A6.
Here, after colliding with the inner wall of the valve housing 8d shown in FIG. 5B, the flow A5 and A6 in the circumferential direction of the valve body toward the discharge ports 803A and 803B pass through the liquid damper chamber described in FIG. It goes to the discharge ports 803A and 803B. As a result, even when the pressure distribution around the valve body 8b is biased, the pressure distribution can be relaxed by the liquid damper chamber.
When the length in the Z-axis direction of the tubular gap 805C formed between the outer periphery of the valve seat member 8A and the inner circumference of the valve housing 8d is z3 and the width is x1, the sectional area of the tubular gap 805C is x1 · z3. Further, when the length of the tapered portion 801 of the valve body 8b is z2, and the width of the top portion of the taper is x1, the cross-sectional area of the tubular gap 805B is (x1 · x2) / 2. Furthermore, when the stroke of the valve body 8b is ST1, this is equal to the length z2 of the tubular gap 805A. If the length of the tubular gap 805A is z1 and the width is x, the sectional area of the tubular gap 805A is z1 · x1.
Here, the sectional area of the tubular gap 805C is made larger than the sectional area of the tubular gap 805B. Specifically, when x1 = 0.8 mm, z1 = 0.4 mm, z2 = 1.7 mm, and z3 = 2.3 mm, the sectional area (1.8 mm 2 ) of the tubular gap 805C is tubular. The cross-sectional area (0.68 mm 2 ) of the gap 805B is set twice or more.
This is because it increases the area of the tubular gap 805B, and if the area of the tapered portion 801 is increased, the pressure receiving area where the pressure pulsation in the tubular gap 805B acts on the valve body 8b increases, which is disadvantageous from the viewpoint of suppressing fluttering. That's why. Further, when the valve body 8b is offset in a direction orthogonal to the sliding direction of the valve body, the cross-sectional area of the tubular gap 805B itself varies and becomes smaller, and the function as a liquid damper may be lowered.
In that respect, by enlarging the tubular gap 805C, these problems can be solved, the cross-sectional area of the liquid damper chamber can be sufficiently increased, and pressure pulsation can be reduced.
In the above example, since the cross-sectional area of the tubular gap 805A is 0.36 mm 2 , the cross-sectional area of the liquid damper chamber is 2.84 mm 2 . Here, to reduce the pressure loss to a predetermined value or less when the engine has a displacement of 1500 cc and a 4-cylinder engine, the cross-sectional area of the liquid damper chamber needs to be 0.3 mm 2 or more. As described above, since the cross-sectional area of only the tubular gap 805A and the tubular gap 805B formed by the tapered portion 801 is 1.04 mm 2 , it is sufficient to reduce the pressure pulsation at the idle flow rate. It is not a sufficient cross-sectional area for the fuel flow rate under load. On the other hand, by adding the tubular gap 805C, the pressure pulsation can be sufficiently reduced even with respect to the fuel flow rate at the maximum load of the engine.
As a method for forming the tubular gap 805B, in addition to providing the tapered portion 801 on the valve body 8b, a method of providing a stepped portion on the valve body 8b can be used as in an embodiment described later. However, in the case of the stepped portion, the flow passing through the sheet portion 8a toward the discharge port 803 becomes a sudden expanded flow, and cavitation may occur. In addition, since the balance of the stepped portion and the flow direction also change abruptly, the loss head is large, and an unintended pressure pulsation may occur, which may promote fluttering.
On the other hand, by providing the valve body 8b with the tapered portion 801 as described above, it is possible to reduce the change in the direction of the discharge flow flowing from the seat portion 8a toward the discharge port 803 while forming the tubular gap 805B. . Thereby, a flow becomes smooth and generation | occurrence | production of the unintended vortex and cavitation can be suppressed.
Here, the sectional area α of the fluid passage is such that α> 0.1 × β with respect to the opening area β when the discharge valve is fully opened. Here, the cross-sectional area α of the fluid passage is a cross-sectional area (0.3 mm 2 ) of the liquid damper chamber that makes the pressure loss equal to or less than a predetermined value at an idle flow rate of a 4-cylinder engine with a displacement of 1500 cc. In addition, the opening area β when the discharge valve is fully opened is a cross-sectional area through which a flow toward the discharge port passes. That is, the opening area β is (the gap length between the valve seat and the seat when the valve is opened (ST1 = 0.4 mm in FIG. 4)) × (the length of the portion of the outer periphery of the valve seat facing the discharge port) (3.75 mm) × 2 (when there are two discharge ports), and 3 mm 2. Therefore, the cross-sectional area α of the fluid passage is larger than the opening area β when the discharge valve is fully open, with α> 0. 1 × β.
Next, the measurement result of the discharge pressure of the high-pressure fuel supply pump according to the present embodiment will be described with reference to FIG.
FIG. 6 is an explanatory diagram of the measurement result of the discharge pressure of the high-pressure fuel supply pump according to the first embodiment of the present invention.
FIG. 6A shows a change of the discharge port pressure P with respect to time t. A pressure P1 indicated by a thin solid line indicates a change in pressure at the discharge port in a high-pressure fuel supply pump having a conventional configuration. Here, the conventional configuration is a case where the tubular gap 8 0 5 B and the tubular gap 8 0 5 C are not provided in the configuration shown in FIG.
On the other hand, the pressure P2 indicated by a thick solid line indicates the pressure change of the discharge port in the high-pressure fuel supply pump according to the present embodiment described with reference to FIGS. The high-pressure fuel supply pump according to the present embodiment, a case where in the configuration shown in FIG. 4, in addition to the tubular gap 8 0 5 A, and a tubular gap 8 0 5 B and the tubular gap 8 0 5 C.
As shown in FIG. 6A, according to the present embodiment, the pressure fluctuation at the discharge port can be reduced.
FIG. 6B shows the pulsation amplitude V of the discharge port pressure obtained by Fourier-transforming the change in pressure shown in FIG. 6A, and the horizontal axis shows the frequency f. The pulsation amplitude V1 indicated by a thin solid line is of a conventional configuration, and the pulsation amplitude V2 indicated by a thick solid line is according to the present embodiment. In the figure, the range from frequency f1 to frequency f2 is the human audible range. In this way, in particular, it is effective in reducing the pulsation amplitude in the audible range, and noise can be reduced.
Next, the assembly process of the discharge valve 8 of this embodiment is demonstrated using FIG.
The discharge valve 8 includes a seat member 8A having the seat portion 8a described in FIG. 2, a valve body 8b, a discharge valve spring 8c, and a valve body housing 8d. These parts are assembled inside the pump housing 1.
Assembling is performed from the left side of the pump housing 1 shown in FIG. As shown in FIG. 1, the electromagnetic suction valve mechanism 30 and the plunger 2 of the pressurizing chamber 11 are assembled inside the pump housing 1. Before these parts are assembled, the pump housing 1 is provided with a hole for incorporating the electromagnetic suction valve mechanism 30. Each component of the discharge valve 8 is inserted from this hole, and the discharge valve 8 is assembled in the internal space on the right side of the pump housing 1 shown in FIG. 2 via the internal space of the pressurizing chamber 11.
First, the valve body housing 8d is press-fitted into the inner space on the right side of the pump housing 1 shown in FIG. At this time, the valve body housing 8d is press-fitted into the pump housing 1 from the left direction in the drawing, and the flange 8d3 of the valve body housing 8d is positioned by contacting the circumferential stepped portion 1a.
Next, the discharge valve spring 8c is inserted into the valve body housing 8d.
Next, the valve body 8b is inserted into the valve body housing 8d.
Finally, the seat member 8A is press-fitted into the pump housing 1 from the left direction shown in the drawing, and the flange portion 8A1 of the valve seat member 8A is positioned by contacting the circumferential stepped portion 1b.
In the above description, the components of the discharge valve 8 are sequentially assembled from the left direction in FIG. 2, that is, from the direction of the pressurizing chamber 11, but may be incorporated from the right direction in FIG. In this case, a hole into which the seat member 8A can be inserted is formed in the right direction of the pump housing 1. From this hole, the seat member 8A is press-fitted and fixed, then the valve body 8b and the discharge valve spring 8c are sequentially inserted, and finally the valve body housing 8d is press-fitted and fixed.
Next, the configuration of the discharge valve unit used as the discharge valve of the high-pressure fuel supply pump according to the present embodiment will be described with reference to FIG.
FIG. 7 is a cross-sectional view showing a configuration of a discharge valve unit used as a discharge valve of the high-pressure fuel supply pump according to the first embodiment of the present invention. 7A and 7B, the movement direction of the valve is the Z axis, and the axes orthogonal to the Z axis are the X axis and the Y axis, respectively. FIG. 7A is a longitudinal sectional view in the ZY plane, and FIG. 7B is a longitudinal sectional view in the ZX plane. 7A and 7B show the opened state of the discharge valve. 7A and 7B, the same reference numerals as those in FIG. 1 denote the same parts.
After the spring 8c and the valve seat 8b are inserted inside the valve housing 8d, the stepped portion 8A3 of the valve seat portion 8a is press-fitted into the inner peripheral surface of the valve housing 8d, whereby the discharge valve unit 8 is integrated. Has been.
As shown in FIG. 2, the discharge valve unit 8U having the above configuration is integrally press-fitted into the pump housing 1 from the direction of the pressurizing chamber 11 in the left direction of FIG. can do. Further, the discharge valve unit 8U can be integrally press-fitted into the pump housing 1 from the right side of the pump unit 1 shown in FIG.
As described above, according to the present embodiment, out of the flow that collides with the valve body from the axial direction and is radially dispersed, the flow toward the range where the discharge port is not formed is transferred to the circumferential liquid damper chamber. Can be directed positively and smoothly toward the discharge port through the fluid passage forming As a result, the pressure distribution around the valve element can be eliminated, the differential pressure acting on the valve element can be reduced, and fluttering can be suppressed.
Even when the valve body is offset in the radial direction from the center of the valve body housing, a circumferential fluid passage (tubular passage 805C) having a cross-sectional area greater than or equal to a predetermined value is formed in advance, so The area change rate can be kept small. As a result, the differential pressure generated on both sides of the valve body can be reduced, and fluttering can be suppressed.
Furthermore, by forming a part of the fluid passage on the surface of a member other than the valve body, the cross-sectional area of the fluid passage is increased without increasing the pressure receiving area where the pressure pulsation in the fluid passage acts on the valve body, Even if a sufficient fluid guiding function in the circumferential direction is achieved and pressure pulsation occurs in the fluid passage, the influence on the valve body behavior can be minimized and fluttering can be suppressed.
In other words, by reducing pressure pulsations in the frequency range where the sensitivity of the human ear is high, avoiding or suppressing the increase in external shape, the complexity of the layout of high-pressure piping, and the associated cost increase, etc. Noise generated with the flow rate can be greatly reduced.
As described above, the influence of noise caused by the flow in the valve body circumferential direction can be reduced.
In the above description, the cylindrical valve body and the valve body housing are used, but fluttering of the valve body can also be performed by forming a fluid passage in the circumferential direction in a similar manner for valves of other shapes. Can be suppressed.
Next, the configuration and operation of the high-pressure fuel supply pump according to the second embodiment of the present invention will be described with reference to FIG. The configuration of the high-pressure fuel supply system using the high-pressure fuel supply pump according to the present embodiment is the same as that shown in FIG.
FIG. 8 is a longitudinal sectional view showing a configuration of a discharge valve used in the high-pressure fuel supply pump according to the second embodiment of the present invention. FIG. 8 shows the opened state of the discharge valve. In FIG. 8, the same reference numerals as those in FIGS. 1 to 4 denote the same parts.
Also in this embodiment, the discharge valve 8 includes a seat portion 8a, a valve body 8b, a discharge valve spring 8c, and a valve body housing 8d. The valve body 8b and the valve body housing 8d are cylindrical, and the discharge ports 803A and 803B are formed at two locations facing the side of the seat portion 8a. Note that three or more discharge ports may be provided in the circumferential direction.
In the present embodiment, the outer diameter of the valve body 8b, that is, the diameter of the portion inserted into the guide portion 8d5 of the valve body housing 8d is configured to be larger than the outer diameter of the seat portion 8a. A stepped portion 802 is provided around 8b2.
With this configuration, a tubular gap 805B is formed between the valve body 8b and the valve body housing 8d. As a result, after colliding with the valve body 8b, the flow toward the area where the discharge ports 803A and 803B are not formed is swung in the circumferential direction of the valve body 8b among the radially dispersed discharge flows, and smoothly approached. It is possible to guide to the discharge ports 803A and 803B. As a result, the uneven pressure distribution around the valve body 8b is alleviated.
As in the first embodiment described with reference to FIG. 4, a tubular gap 805C is formed between the outer peripheral portion of the seat portion 8a and the inner diameter portion of the valve body housing 8d. By providing the tubular gap 805C in addition to the tubular gap 805B, a sufficient cross-sectional area can be secured without increasing the pressure receiving area where the pressure pulsation in the tubular gap acts on the valve body 8b, and fluttering of the valve body 8b can be achieved. It can suppress and can reduce noise. In addition, the cross-sectional area of the tubular gap 805C is larger than the cross-sectional area of the tubular gap 805B, and the pressure receiving area where pressure pulsation acts can be reduced.
With the configuration described above, the influence of noise caused by the flow in the circumferential direction of the valve body can be reduced also in this embodiment.
Next, the configuration and operation of the high-pressure fuel supply pump according to the third embodiment of the present invention will be described with reference to FIG. The configuration of the high-pressure fuel supply system using the high-pressure fuel supply pump according to the present embodiment is the same as that shown in FIG.
FIG. 9 is a longitudinal sectional view showing the configuration of the discharge valve used in the high-pressure fuel supply pump according to the third embodiment of the present invention. FIG. 9 shows the opened state of the discharge valve. In FIG. 9, the same reference numerals as those in FIGS. 1 to 4 denote the same parts.
In the present embodiment, a plate-like valve body 8b in which the guide portion 806 in the embodiment shown in FIGS. 2 and 8 is not provided is used. When the plate-like valve body 8b is used, the structure and processing are easy and advantageous in cost reduction, compared to the case where the valve body with a guide portion as in the embodiment shown in FIGS. 2 and 8 is used. . However, since there is no mechanism for suppressing unintended valve behavior when it occurs, suppression of fluttering is essential not only from noise reduction but also from the viewpoint of operational reliability.
As in the case of the valve body with guide, the outer diameter of the valve body 8b is configured to be larger than the outer diameter of the seat portion 8a, and a tapered portion 807 is provided. Thereby, the tubular gap 805B is formed, a smooth flow can be generated in the circumferential direction, and the uneven pressure distribution can be reduced. Further, by providing the taper 807, the change in the direction of the main flow in the radial direction toward the discharge ports 803A and 803B can be reduced and smoothed.
The present invention is not limited to high-pressure fuel supply pumps for internal combustion engines, and can be widely used for various high-pressure pumps.
1 is an overall configuration diagram of a high-pressure fuel supply system using a high-pressure fuel supply pump according to a first embodiment of the present invention. It is a longitudinal cross-sectional view which shows the structure of the discharge valve used for the high pressure fuel supply pump by the 1st Embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the discharge valve used for the high pressure fuel supply pump by the 1st Embodiment of this invention. It is a principal part expanded sectional view which shows the structure of the discharge valve used for the high pressure fuel supply pump by the 1st Embodiment of this invention. It is explanatory drawing of the flow of the fuel in the discharge valve used for the high pressure fuel supply pump by the 1st Embodiment of this invention. It is explanatory drawing of the flow of the fuel in the discharge valve used for the high pressure fuel supply pump by the 1st Embodiment of this invention. It is explanatory drawing of the measurement result of the discharge pressure of the high pressure fuel supply pump by the 1st Embodiment of this invention. It is explanatory drawing of the measurement result of the discharge pressure of the high pressure fuel supply pump by the 1st Embodiment of this invention. It is sectional drawing which shows the structure of the discharge valve unit used as a discharge valve of the high pressure fuel supply pump by the 1st Embodiment of this invention. It is sectional drawing which shows the structure of the discharge valve unit used as a discharge valve of the high pressure fuel supply pump by the 1st Embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the discharge valve used for the high pressure fuel supply pump by the 2nd Embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the discharge valve used for the high pressure fuel supply pump by the 3rd Embodiment of this invention.
DESCRIPTION OF SYMBOLS 1 ... Pump housing 1a, 1b ... Circumferential step part 2 ... Plunger 8 ... Discharge valve 8A ... Seat member 8A1 ... Flange part 8A2 ... Step part 8a ... Seat part 8b ... Valve body 8b
8b1 ... recess 8b2 ... valve seat 8c ... discharge valve spring 8d ... valve housing 8d1 ... guide peripheral surface 8d2 ... cut flat part 8d3 ... flange part 8d4 ... equal pressure hole 8d5 ... guide part 8d6 ... step part 9 ... reduction of pressure pulsation Mechanism 10c ... Suction passage 11 ... Pressure chamber 13 ... Discharge port 20 ... Fuel tank 23 ... Common rail 24 ... Injector 26 ... Pressure sensor 27 ... ECU
30 ... Electromagnetic suction valve mechanisms 801, 807 ... Tapered portion 802 ... Stepped portions 803A, 803B ... Discharge port 805 ... Liquid damper chambers 805A, 805B, 805C ... Tubular passage
A pressurizing chamber whose volume is changed by the reciprocating motion of the plunger;
A discharge port for discharging fuel pressurized by the pressurizing chamber;
A discharge valve that is provided between the discharge port and the pressurizing chamber and is a check valve;
The discharge valve is
A valve body housing in which a plurality of discharge ports communicating with the discharge port are formed;
A valve body housed inside the valve body housing and biased in a direction to close the valve by a discharge valve spring;
A high-pressure fuel supply pump that is housed in the valve body housing and includes a seat member having a seat portion that contacts the valve body and closes the valve;
The surface of the valve seat formed on the valve body and the surface of the seat part are flat valves that are parallel to a plane perpendicular to the axial direction of the valve body,
When the valve is opened, the flow of fuel that has collided with the valve body from the axial direction through the hollow portion of the seat member from the pressurizing chamber is radially dispersed in the radial direction of the valve body and directly directed to the discharge port. After colliding with the flow and the inner wall of the valve housing, it becomes the flow in the circumferential direction of the valve body toward the discharge port,
Formed between the outer periphery of the seat member and the outer periphery of the valve body and the inner periphery of the valve housing, and includes a liquid damper chamber for the flow in the circumferential direction, the liquid damper chamber including the outer periphery of the valve body and the And a first tubular passage formed between the inner periphery of the valve housing and a second tubular passage formed between the outer periphery of the seat member and the inner periphery of the valve housing. High pressure fuel supply pump.
The high-pressure fuel supply pump according to claim 1,
The first and second tubular passages are:
A high-pressure fuel supply pump characterized in that a cross-sectional area of the second tubular passage in a plane including the axis of the valve body is larger than a cross-sectional area of the first tubular passage.
The high-pressure fuel supply pump according to claim 2,
The high-pressure fuel supply pump according to claim 1, wherein an outer diameter of the valve body is larger than an outer diameter of the valve seat.
The high-pressure fuel supply pump according to claim 3,
The high pressure fuel supply pump, wherein the first tubular passage is formed between a taper provided on an outer periphery of the valve seat of the valve body and an inner periphery of the valve housing.
The liquid damper chamber has a cross-sectional area in a plane including the axis of the valve body that is larger than 0.3 mm 2 .
Used in a high-pressure fuel supply pump that discharges fuel pressurized by a pressurizing chamber from a discharge port via a discharge valve that is a check valve,
A discharge valve unit that is press-fitted into a valve body housing that constitutes a part of the discharge valve,
The discharge valve unit is
A valve body biased in a direction to close the valve by a discharge valve spring;
A seat member having a seat portion that contacts the valve body and closes the valve;
The discharge valve is a flat valve in which the surface of the valve seat formed on the valve body and the surface of the seat portion are parallel to a plane perpendicular to the axial direction of the valve body,
When the valve is opened, the flow of the fuel colliding with the valve body from the axial direction through the hollow portion of the seat member from the pressurizing chamber is radially dispersed in the radial direction of the valve body and flows directly to the discharge port. And after colliding with the inner wall of the valve housing, it becomes a flow in the circumferential direction of the valve body toward the discharge port,
Formed between the outer periphery of the seat member and the outer periphery of the valve body and the inner periphery of the valve housing, and includes a liquid damper chamber for the flow in the circumferential direction, the liquid damper chamber including the outer periphery of the valve body and the And a first tubular passage formed between the inner periphery of the valve housing and a second tubular passage formed between the outer periphery of the seat member and the inner periphery of the valve housing. Discharge valve unit.
JP2011500416A 2009-02-20 2009-02-20 High pressure fuel supply pump and discharge valve unit used therefor Active JP5180365B2 (en)
PCT/JP2009/053077 WO2010095247A1 (en) 2009-02-20 2009-02-20 High-pressure fuel feed pump, and discharge valve unit used therein
JPWO2010095247A1 JPWO2010095247A1 (en) 2012-08-16
JP5180365B2 true JP5180365B2 (en) 2013-04-10
ID=42633547
JP2011500416A Active JP5180365B2 (en) 2009-02-20 2009-02-20 High pressure fuel supply pump and discharge valve unit used therefor
US (1) US8740579B2 (en)
EP (1) EP2302195B1 (en)
JP (1) JP5180365B2 (en)
CN (1) CN102325987B (en)
WO (1) WO2010095247A1 (en)
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2009-02-20 CN CN200980156950.0A patent/CN102325987B/en active IP Right Grant
2009-02-20 US US12/674,145 patent/US8740579B2/en active Active
2009-02-20 JP JP2011500416A patent/JP5180365B2/en active Active
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