CN113692487B - High-pressure fuel pump - Google Patents
High-pressure fuel pump Download PDFInfo
- Publication number
- CN113692487B CN113692487B CN202080028729.3A CN202080028729A CN113692487B CN 113692487 B CN113692487 B CN 113692487B CN 202080028729 A CN202080028729 A CN 202080028729A CN 113692487 B CN113692487 B CN 113692487B
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- China
- Prior art keywords
- valve
- suction valve
- pressure fuel
- valve body
- fuel pump
- Prior art date
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- 239000000446 fuel Substances 0.000 title claims abstract description 92
- 230000007246 mechanism Effects 0.000 claims abstract description 50
- 230000002093 peripheral effect Effects 0.000 claims abstract description 23
- 230000009467 reduction Effects 0.000 abstract description 3
- 238000007789 sealing Methods 0.000 abstract description 3
- 230000000087 stabilizing effect Effects 0.000 abstract description 3
- 238000010586 diagram Methods 0.000 description 8
- 230000007423 decrease Effects 0.000 description 4
- 230000004323 axial length Effects 0.000 description 3
- 239000002828 fuel tank Substances 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000010349 pulsation Effects 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000003746 surface roughness Effects 0.000 description 2
- 230000001174 ascending effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 102220098272 rs878853037 Human genes 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
Abstract
The purpose of the present invention is to suppress the reduction in durability and oil sealing performance of a suction valve mechanism by stabilizing the operation of the suction valve. Accordingly, the high-pressure fuel pump (100) of the present invention includes an electromagnetic suction valve mechanism having a suction valve (30), the suction valve (30) including: a rod (30B); a valve body (30A) integrally formed with the stem (30B); a1 st guide part (31B) for guiding the outer peripheral part (30B 1) of the lever part (30B); and a2 nd guide part (34B 1) for guiding the outer periphery of the valve body part (30A).
Description
Technical Field
The present invention relates to a high-pressure fuel pump including a suction valve mechanism.
Background
As background art in the art, a high-pressure fuel supply pump described in japanese patent application laid-open No. 2017-96216 (patent document 1) is known. The high-pressure fuel supply pump of patent document 1 includes an electromagnetically driven intake valve mechanism, and the following structure is described in paragraphs 0018 to 0021 of patent document 1. The electromagnetically driven suction valve mechanism includes a plunger rod that is electromagnetically driven. A valve is provided at the front end of the plunger rod, the valve being opposed to a valve seat formed in the valve housing. A plunger rod biasing spring is provided at the other end of the plunger rod to bias the plunger rod in a direction to separate the valve from the valve seat (valve opening direction). A valve stopper is fixed to the outer peripheral portion of the valve housing on the front end side.
The valve stopper is a member that restricts movement of the valve 203 in the valve opening direction. A valve biasing spring is disposed between the valve and the valve stopper, and the valve is biased in a direction away from the valve stopper (valve closing direction) by the valve biasing spring. The distal ends of the valve and the plunger rod are biased in opposite directions by respective springs, but since the plunger rod biasing spring is constituted by a strong spring, the plunger rod presses the valve in a direction away from the valve seat against the force of the valve biasing spring, and as a result, presses the valve against the valve stopper.
The plunger rod and valve are not fixed and the front end of the plunger rod is sized in such a way as to be able to move away from the valve (paragraph 0045). The valve stopper has a protruding portion in a center portion thereof, the protruding portion including a cylindrical surface portion protruding toward a bottomed cylindrical portion side of the valve, the cylindrical surface portion functioning as a guide portion for guiding a stroke of the valve in an axial direction (paragraph 0047).
Prior art literature
Patent literature
Patent document 1: japanese patent laid-open No. 2017-96216
Disclosure of Invention
Problems to be solved by the invention
The high-pressure fuel supply pump of patent document 1 is configured such that a plunger rod and a valve of an electromagnetic drive type suction valve mechanism are not fixed, and the valve is guided by a cylindrical surface portion of a projection provided in a valve stopper to a stroke in an axial direction. In this case, the axial length of the cylindrical surface portion needs to be increased in order to stabilize the operation of the valve in the axial direction, but if the axial length of the cylindrical surface portion is increased, the suction valve mechanism becomes larger. In other words, if the axial length of the cylindrical surface portion is shortened, the linear motion of the valve in the axial direction becomes unstable, and the valve comes into contact with the valve seat in a state where the valve is tilted. In this case, wear of the valve seat portion of the valve (suction valve) or the valve seat (suction valve seat) becomes severe, and the durability of the suction valve mechanism is reduced, leading to a reduction in oil tightness performance.
The purpose of the present invention is to suppress the reduction in durability and oil sealing performance of a suction valve mechanism by stabilizing the operation of the suction valve.
Means for solving the problems
In order to solve the above problems, the high-pressure fuel pump of the present invention,
comprising an electromagnetic suction valve mechanism with a suction valve,
the suction valve includes:
a stem portion;
a valve body integrally formed with the stem;
a1 st guide portion for guiding an outer peripheral portion of the lever portion; and
and a2 nd guide part for guiding the outer periphery of the valve body.
Effects of the invention
According to the present invention, by stabilizing the operation of the suction valve, it is possible to suppress a decrease in durability and oil sealing performance of the suction valve mechanism. Other structures, operations, and effects of the present invention are described in detail in the following examples.
Drawings
Fig. 1 is an overall construction diagram of an engine system to which the high-pressure fuel pump of the present invention is applied.
Fig. 2 is a cross-sectional view showing a vertical cross-section (a cross-section parallel to the axial direction of the plunger) of the high-pressure fuel pump as a precondition for applying the present invention.
Fig. 3 is a cross-sectional view showing a horizontal cross section (a cross section orthogonal to the axial direction of the plunger) of the high-pressure fuel pump of fig. 2 as viewed from above.
Fig. 4 is a cross-sectional view showing a vertical cross section (a cross section parallel to the axial direction of the plunger) of the high-pressure fuel pump of fig. 2, as viewed from a direction different from that of fig. 2.
Fig. 5 is a sectional view showing the electromagnetic suction valve mechanism of fig. 2 in an enlarged manner.
Fig. 6 is a diagram for explaining the operation of the suction valve.
Fig. 7 is a diagram showing an example of a modification of the structure of the valve body and the guide portion for guiding the valve body.
Fig. 8 is a diagram showing an example of a modification of the structure of the valve body and the guide portion for guiding the valve body.
Detailed Description
Hereinafter, examples of the present invention will be described.
Fig. 1 is an overall configuration diagram of an engine system to which a high-pressure fuel pump 100 of the present invention is applied. The portion surrounded by the broken line represents the main body of the high-pressure fuel pump 100 (refer to fig. 2), and the mechanism and the components shown in the broken line represent the integral assembly to the pump body 1. Fig. 1 is a diagram schematically showing an operation of an engine system.
In the following description, the vertical direction is sometimes designated for explanation, but the vertical direction is based on the vertical direction in fig. 2 and 4, and does not necessarily coincide with the vertical direction in the case where high-pressure fuel pump 100 is mounted to the engine. In the following description, the axial direction is defined by the central axis 2A (see fig. 2) of the plunger 2, and the axial direction is parallel to the central axis 2A of the plunger 2 and coincides with the longitudinal direction of the plunger 2.
The fuel of the fuel tank 20 is drawn by the feed pump 21 based on a signal from an engine control unit 27 (hereinafter, ECU). The fuel is pressurized to an appropriate supply pressure and delivered to the low-pressure fuel suction port 10a of the high-pressure fuel pump 100 through the suction pipe 28. The low-pressure fuel suction port 10a is constituted by a suction joint 51 (see fig. 3 and 4).
The fuel having passed through the low-pressure fuel suction port 10a reaches the suction port 31b of the electromagnetic suction valve mechanism 300 constituting the capacity variable mechanism via buffer chambers (10 b, 10 c) in which the pressure pulsation reducing mechanism 9 is disposed.
The fuel flowing into the electromagnetic intake valve mechanism 300 flows into the pressurizing chamber 11 through the intake port (intake passage) opened and closed by the intake valve 30. The reciprocating power is applied to the plunger 2 by a cam mechanism 93 (see fig. 2 and 4) of the engine. By the reciprocation of the plunger 2, the fuel is sucked into the pressurizing chamber 11 from the suction port opened and closed by the suction valve 30 in the descending stroke of the plunger 2. The fuel sucked into the pressurizing chamber 11 is pressurized in the ascending stroke. The pressurized fuel is pressure-fed to the common rail 23 to which the pressure sensor 26 is attached via the discharge valve mechanism 8.
The injector 24 connected to the common rail 23 injects fuel to the engine based on a signal from the ECU 27. The high-pressure fuel pump of the present embodiment is a high-pressure fuel pump suitable for a so-called direct injection engine system in which the injector 24 directly injects fuel into the cylinder of the engine. The high-pressure fuel pump 100 controls the electromagnetic suction valve mechanism 300 by a signal sent from the ECU27, and discharges a desired fuel flow rate through the fuel discharge port 12.
Fig. 2 is a cross-sectional view showing a vertical cross-section (a cross-section parallel to the axial direction of the plunger 2) of the high-pressure fuel pump 100 as a precondition for application of the present invention. Fig. 3 is a cross-sectional view showing a horizontal cross-section (a cross-section orthogonal to the axial direction of the plunger 2) of the high-pressure fuel pump 100 of fig. 2 as viewed from above. Fig. 4 is a cross-sectional view showing a vertical cross-section (a cross-section parallel to the axial direction of the plunger 2) of the high-pressure fuel pump 100 of fig. 2 as viewed from a direction different from that of fig. 2.
A cylinder 6 that guides the reciprocating motion of the plunger 2 and forms a pressurizing chamber 11 together with the pump body 1 is mounted on the pump body 1. That is, the plunger 2 reciprocates inside the cylinder 6 to change the volume of the pressurizing chamber 11. The pump body 1 is provided with an electromagnetic intake valve mechanism 300 for supplying fuel to the pressurizing chamber 11 and a discharge valve mechanism 8 for discharging fuel from the pressurizing chamber 11 to the discharge passage. The cylinder 6 is press-fitted into the pump body 1 on the outer peripheral side thereof.
A tappet 92 for converting a rotational motion of a cam 93 attached to a camshaft of the internal combustion engine into an up-down motion and transmitting the same to the plunger 2 is provided at a lower end of the plunger 2. Plunger 2 is pressed against tappet 92 by plunger urging spring 4 through retainer 15. Accordingly, the plunger 2 can be reciprocated up and down by the rotational movement of the cam 93.
A suction joint 51 is attached to a side surface of the pump body 1 of the high-pressure fuel pump 100. The suction joint 51 is connected to a low-pressure pipe for supplying fuel from the fuel tank 20 to the high-pressure fuel pump 100, and fuel is supplied from the suction joint 51 to the inside of the high-pressure fuel pump 100. The intake filter 52 prevents foreign matter that exists between the fuel tank 20 and the low-pressure fuel intake port 10a from being absorbed into the inside of the high-pressure fuel pump 100 by the flow of fuel.
The fuel having passed through the low-pressure fuel suction port 10a passes through a low-pressure fuel suction passage provided in the pump body 1 so as to extend in the up-down direction, and is delivered to the pressure pulsation reducing mechanism 9. The pressure pulsation reducing mechanism 9 is disposed in the buffer chambers 10b and 10c between the buffer cover 14 and the upper end surface of the pump body 1.
The fuel having passed through the buffer chambers 10b and 10c then reaches the suction port 31b of the electromagnetic suction valve mechanism 300 via the low-pressure fuel suction passage 10d formed to extend in the up-down direction in the pump body 1. Further, the suction port 31b is formed in the suction valve seat member 31 forming the suction valve seat 31 a.
The electromagnetic suction valve mechanism 300 is provided with a terminal 46a. The terminal 46a is integrally molded with the connector 46, and an unmolded end can be connected to the engine control unit 27 side.
The electromagnetic suction valve mechanism 300 will be described in detail with reference to fig. 3.
When in the intake stroke state, the volume of the pressurizing chamber 11 increases, and the fuel pressure in the pressurizing chamber 11 decreases. In this stroke, if the fuel pressure in the pressurizing chamber 11 is lower than the pressure of the suction port 31b, the suction valve 30 is in the valve-opened state. When the suction valve 30 is brought into the maximum lift state, the suction valve 30 contacts the stopper 32. By lifting the suction valve 30, the suction port opening between the suction valve seat 31a and the suction valve 30, the electromagnetic suction valve mechanism 300 opens. The fuel flows into the pressurizing chamber 11 through a hole (fuel passage) formed in the pump body 1 in the lateral direction (horizontal direction) through a suction port between the suction valve seat 31a and the suction valve 30.
After the end of the intake stroke, the plunger 2 is turned into an upward movement and is transferred to the upward stroke. Here, the electromagnetic coil 43 maintains the non-energized state, and does not apply a magnetic force. The armature urging spring 40 urges the armature (anchor) 36 in the right direction (valve opening direction) in the drawing, and urges the intake valve 30 in the valve opening direction via the armature 36. The armature biasing spring 40 sets the biasing force so as to have a sufficient biasing force required to maintain the intake valve 30 open in a state where the electromagnetic coil 43 is not energized. The volume of the pressurizing chamber 11 decreases with the upward movement of the plunger 2, but in this state, the fuel once sucked into the pressurizing chamber 11 returns again to the suction passage 10d through the suction port of the suction valve 30 in the valve-opened state, so the pressure of the pressurizing chamber 11 does not rise. This stroke is referred to as the return stroke.
In this state, when a control signal from the ECU27 is applied to the solenoid valve mechanism 300, a current flows through the solenoid 43 via the terminal 46 (refer to fig. 2). Thereby, a magnetic attractive force acts between the core 39 and the armature 36, and the core 39 and the armature 36 are in contact with each other at a magnetic attractive surface. The magnetic attractive force biases the armature 36 against the biasing force of the armature biasing spring 40, and moves the armature 36 in a direction away from the intake valve 30.
At this time, the suction valve 30 is closed by the biasing force of the suction valve biasing spring 33 and the fluid force generated by the fuel flowing into the suction passage 10 d. After the valve is closed, the fuel pressure in the pressurizing chamber 11 increases with the upward movement of the plunger 2, and when the fuel pressure exceeds the pressure in the fuel discharge port 12, the high-pressure fuel is discharged through the discharge valve mechanism 8, and the high-pressure fuel is supplied to the common rail 23. This stroke is referred to as the discharge stroke.
That is, the upward stroke from the lower start point to the upper start point of the plunger 2 is composed of the return stroke and the discharge stroke. Then, by controlling the timing of energization to the coil 43 of the electromagnetic intake valve mechanism 300, the amount of high-pressure fuel discharged can be controlled.
As shown in fig. 3, the discharge valve mechanism 8 provided at the outlet of the pressurizing chamber 11 is constituted by a discharge valve seat 8a, a discharge valve 8b that is in contact with and separated from the discharge valve seat 8a, a discharge valve spring 8c that biases the discharge valve 8b toward the discharge valve seat 8a, and a discharge valve stopper 8d that determines the stroke (moving distance) of the discharge valve 8 b. The discharge valve stopper 8d is joined to the pump body 1 at the abutting portion 8e by welding, and blocks the flow path of the fuel flow from the outside.
In a state where there is no fuel differential pressure between the pressurizing chamber 11 and the discharge valve chamber 12a, the discharge valve 8b is pressed against the discharge valve seat 8a by the urging force of the discharge valve spring 8c, and is in a valve-closed state. When the fuel pressure in the pressurizing chamber 11 becomes larger than the fuel pressure in the discharge valve chamber 12a, the discharge valve 8b opens against the discharge valve spring 8 c. The fuel discharge port 12 is formed in the discharge joint 60, and the discharge joint 60 is welded and fixed to the pump body 1 by a welded portion 60 a.
Next, the relief valve mechanism 200 will be described with reference to fig. 2.
The relief valve mechanism 200 is composed of a relief valve body 201, a relief valve 202, a relief valve holder 203, a relief spring 204, and a spring stopper 205. The relief valve 202 receives the load of the relief spring 204 via the relief valve holder 203, is pressed by the valve seat portion of the relief valve body 201, and cuts off the fuel in cooperation with the valve seat portion.
If the pressure of the fuel discharge port 12 becomes abnormally high due to a failure of the electromagnetic suction valve mechanism 300 of the high-pressure fuel pump 100 or the like and becomes greater than the set pressure of the relief valve mechanism 200, the abnormally high pressure fuel is overflowed to the relief chamber 10c as the low pressure side via the relief passage 213. In the present embodiment, the relief destination of the relief valve mechanism 200 is the buffer chamber 10c, but may be configured to relief to the pressurizing chamber 11.
The electromagnetic suction valve mechanism 300 will be described in more detail with reference to fig. 5. Fig. 5 is a sectional view showing the electromagnetic suction valve mechanism 300 of fig. 2 in an enlarged manner.
The suction valve 30 is composed of a valve body 30A, a stem 30B, and a guided portion (projection) 30C. In the present embodiment, the guided portion 30C is regarded as a part of the valve body 30A, and the guided portion 30C is formed in the valve body 30A. The outer diameter Φ30a of the valve body 30A is larger than the outer diameter of the stem 30B, the valve body 30A forms a large diameter portion with respect to the stem 30B, and the stem 30B forms a small diameter portion with respect to the valve body 30A.
The rod portion 30B has a rod shape (a round rod shape or a cylindrical shape) with a circular cross section. The valve body 30A is formed in a circular plate shape or a cylindrical shape having a thickness D30A smaller than the outermost diameter Φ30a in the axial direction (longitudinal direction) of the stem 30B. The axial direction of the rod portion 30B is integrally formed with the valve body portion 30A so as to be orthogonal to the end surface 30A1 of the valve body portion 30A. The stem 30B and the valve body 30A may be integrally formed, or may be joined to each other by a member constituting the stem 30B and a member constituting the valve body 30A.
The end surface 30A1 of the valve body 30A constitutes a seat portion for a fuel seal portion, which is opposed to the valve seat portion 31a formed in the suction valve seat member 31. Therefore, the valve seat portion 30A1 of the valve body portion 30A is finished to have a high surface accuracy (i.e., a small surface roughness).
The outer cylindrical surface (outer peripheral surface) 30B1 of the stem 30B constitutes a guided portion (1 st guided portion) that guides the movement of the stem 30B in the axial direction (longitudinal direction) by a guide portion (1 st guide portion) 31B formed in the suction valve seat member 31. The guide portion 31B is formed on the inner cylindrical surface (inner peripheral surface) of the suction valve seat member 31. The outer peripheral surface 30B1 of the stem portion 30B and the inner peripheral surface 31B of the suction valve seat member 31 are finished to have high surface accuracy (i.e., small surface roughness). This makes it possible to suppress the fixation and abrasion with the inner cylindrical portion of the guide portion 31B when the lever portion 30B and the guide portion 31B slide.
A convex portion 30C is formed on a surface (end surface) 30A2 of the valve body 30A opposite to the valve seat portion 30A 1. A valve stopper 34 is provided on the end surface 30A2 and the convex portion 30C side of the valve body 30A. The valve stopper 34 surrounds the valve body 30A by a side wall (peripheral wall) 34A2 of the large-diameter recess 34A, and constitutes a valve body housing accommodating the valve body 30A. In addition, the valve stopper 34 has at least 2 layers of stepped concave portions as viewed from the suction valve seat member 31 side so as to house the valve body portion 30A and the convex portion 30C.
A bottom surface (opening side concave bottom surface) 34A1 of the large diameter concave portion (opening side concave portion) 34A of the valve stopper 34 abuts against an end surface 30A2 of the valve body portion 30A, and constitutes a stopper portion (stopper surface) that restricts movement of the valve body portion 30A in the valve opening direction. The bottom surface (bottom surface of the back side concave portion) 34B2 of the small diameter concave portion (back side concave portion) 34B of the valve stopper 34 constitutes a spring seat of the suction valve biasing spring 33.
The suction valve biasing spring 33 is disposed between the small-diameter concave bottom surface 34B2 and the end surface 30C1 of the convex portion 30C, and biases the entire suction valve 30 in the valve closing direction via the valve body portion 30A. The suction valve urging spring 33 is in direct contact with the bottom surface 34B2 of the valve stopper 34. The bottom surface 34B2 of the valve stopper 34 is orthogonal to the center axis LA of the guide portion 31B formed in the suction valve seat member 31, and prevents the suction valve biasing spring 33 from being mounted obliquely.
The valve stopper 34 has 1 or more openings (notched portions) 34D for constituting the fuel flow path. The opening (notch) 34D for constituting the fuel flow path provided in the valve stopper 34 may have a hole shape or a groove shape.
The inner diameter of the small-diameter concave portion 34B of the valve stopper 34 is slightly larger than the outer diameter Φ30c of the convex portion 30C, and the outer peripheral surface (guided portion) 30C2 of the convex portion 30C slides on the inner cylindrical portion (inner peripheral surface) 34B1 of the small-diameter concave portion 34B. That is, the outer peripheral surface 30C2 of the protruding portion 30C constitutes a guided portion (2 nd guided portion), and the inner peripheral surface 34B1 constitutes a guide portion (guide surface) that guides the guided portion 30C2. In this way, in the suction valve 30, the guided portion 30C2 of the protruding portion 30C provided at one end portion is guided to move in the axial direction by the guide portion (2 nd guide portion) 34B1 of the valve stopper 34.
The suction valve 30 is supported at both ends of a stem portion 30B and a projection portion 30C by a guide portion 31B formed on the suction valve seat member 31 and a guide portion 34B1 formed on the valve stopper 34, respectively, and the radial movement and the inclination range are restricted. The guide portion 31B formed in the suction valve seat member 31 and the guide portion 34B1 formed in the valve stopper 34 are provided with clearances with respect to the guided portion 30B1 of the lever portion 30B and the guided portion 30C2 of the convex portion 30C, respectively, and the suction valve 30 is slidable with respect to the guide portion 31B and the guide portion 34B1 in an environment where the sliding resistance is small.
The suction valve seat member 31 is provided with a fuel seal portion 31a orthogonal to the center axis LA of the guide portion 31B, and the surface accuracy of the surface is made small.
The valve stopper 34 will be explained again. The valve stopper 34 has a stopper surface 34A1 and a surface 34E in surface contact with the suction valve seat member 31, and a valve body portion 30A including a convex portion 30C is accommodated between these surfaces 34A1, 34E, and the distance between the stopper surface 34A1 and the surface 34E is Δl. If the thickness of only the valve body 30A other than the convex portion 30C is t30A, the value g1 (see fig. 6) of Δl—t30a can be adjusted to the stroke length of the intake valve 30. The suction valve 30 is prevented from sticking to the valve stopper 34 by reducing the contact area between the valve stopper 34 and the valve body 30A by providing the tapered portion 34A3 on the valve stopper 34 side of the suction valve 30. In addition, the fuel passage area is increased by providing the tapered portion 34 A3. Further, by providing the tapered portion 34A3, the fluid resistance at the time of valve opening is reduced, and the valve opening operation is stabilized.
The suction valve seat member 31 is pushed or inserted into the inner cylindrical portion 1H2 (see fig. 3) provided in the pump body 1. The valve stopper 34 is pressed or inserted into the inner cylindrical portion 1H1 provided in the pump body 1. The inner cylindrical portions 1H1 and 1H2 provided in the pump body 1 are coaxially manufactured, and the better the coaxial accuracy is, the higher the coaxial accuracy of the suction valve 30 and the guide portions 31B and 34B1 can be.
The smaller the length of the guide portion 31B of the suction valve seat member 31 in the axial direction is, the smaller the sliding area with the suction valve 30 can be suppressed. In addition, the smaller the length of the guide portion 34B1 of the valve stopper 34 in the axial direction is, the smaller the sliding area with the suction valve 30 can be suppressed. Further, by forming the convex portion 30C into a spherical shape, when the suction valve 30 and the valve seat portion 31a are closed, the suction valve 30 can be inclined in accordance with the relative positional displacement after assembly of the components of the suction valve 30 and the valve seat portion 31a, and abrasion due to the contact of one end of the suction valve 30 and the increase in the contact surface pressure of the corner portion of the guide portion 31B of the suction valve seat member 31 and the lever portion 30B can be suppressed.
Fig. 6 is a diagram for explaining the operation of the suction valve 30. Fig. 6 (a) shows a state when the valve is opened. Fig. 6 (B) shows a state in the middle of transition from the valve-open state to the valve-closed state. Fig. 6 (C) shows a state when the valve is closed.
In the state of fig. 6 (a), the gap G1 between the valve seat portion 30A1 and the valve seat portion 31a of the valve body portion 30A is G1, and the gap G3 between the end surface 36A of the armature 36 and the end surface 39A of the core 39 is G2. In this case, g2 is greater than g1 (g 2 > g 1). The end 30B2 of the rod portion abuts against the end surface 36B of the armature 36, and the gap G2 between the end 30B2 and the end surface 36B is 0 (g2=0).
In the state of fig. 6B, the gap G1 between the valve seat portion 30A1 and the valve seat portion 31a of the valve body portion 30A is 0 (g1=0), and the gap G3 between the end surface 36A of the armature 36 and the end surface 39A of the core 39 is G3. In this case, g3 is a size obtained by subtracting g1 from g2 (g3=g2—g1). The end 30B2 of the rod portion abuts against the end surface 36B of the armature 36, and the gap G2 between the end 30B2 and the end surface 36B is 0 (g2=0).
In the state of fig. 6C, the gap G1 between the valve seat portion 30A1 and the valve seat portion 31a of the valve body portion 30A is 0 (g1=0), and the gap G3 between the end face 36A of the armature 36 and the end face 39A of the core 39 is also 0 (g3=0). In this case, the end portion 30B2 of the stem portion and the end face 36B of the armature 36 are separated in the direction along the central axis LA, a gap is generated between the end portion 30B2 of the stem portion and the end face 36B of the armature 36, and the gap G2 between the end portion 30B2 and the end face 36B becomes G3.
The deformation of the structure of the valve body 30A and the guide portion guiding the valve body 30A will be described. Fig. 7 and 8 are diagrams showing an example of a modification of the structure of the valve body 30A and the guide portion for guiding the valve body 30A.
In fig. 7, the protruding portion 31C is not provided, and the outermost peripheral portion (outer peripheral surface having the largest outer diameter) of the valve body 30A is defined as the guided portion 30C2. In this case, 30C2 is not the outer peripheral surface of the convex portion 31C.
In this example, the suction valve seat member 31 constitutes both the 1 st guide portion 31B and the 2 nd guide portion 34B1. For example, a portion of the side wall (peripheral wall) 34A2 of the valve stopper 34 may be constituted by the suction valve seat member 31. In this case, the 1 st guided portion 31B1 is also formed in the lever portion 31B, and the 2 nd guided portion 30C2 is formed in the valve body portion 30A. In this example, the coaxiality of the 1 st guide portion 31B and the 2 nd guide portion 34B1 is also maintained. As long as the coaxiality of the 1 st guide portion 31B and the 2 nd guide portion 34B1 is maintained, other members constituting the 1 st guide portion 31B may be provided without providing the 1 st guide portion 31B to the suction valve seat member 31.
In fig. 8, in fig. 7, as in the embodiment of fig. 5, a1 st guide portion 31B formed in the suction valve seat member 31 is provided in a valve stopper (valve housing) 34. In this case, the 2 nd guided portion 30C2 is configured in the same manner as in fig. 7.
In the example illustrated in fig. 7 or 8, the 2 nd guide portion 34B1 provided in the suction valve seat member 31 or the valve stopper (valve housing) 34 may be formed in the pump body 1. In this case, by directly forming the shape of the valve stopper 34 to the pump body 1, it is not necessary to prepare other members for the valve stopper 34 and assemble them to the pump body 1. This can improve the efficiency of the assembly operation and reduce the material cost.
The features of the high-pressure fuel pump 100 of the present embodiment are, for example, the following features.
(1) Comprising an electromagnetic suction valve mechanism 300 having a suction valve 30, the suction valve 30 comprising: a lever portion 30B; a valve body portion 30A integrally formed with the stem portion 30B; a1 st guide portion 31B that guides an outer peripheral portion 30B1 of the lever portion 30B; and a2 nd guide portion 34B1 that guides the outer periphery of the valve body portion 30A.
(2) In (1), the 2 nd guide portion 34B1 guides the outer periphery of the convex portion 30C formed on the front end side of the valve body portion 30A.
(3) In (1), the 1 st guide portion 31B is configured coaxially with the 2 nd guide portion 34B1.
(4) In (3), the suction valve seat member 31 is provided to seat the valve body 30A, and the 1 st guide portion 31B is constituted by the suction valve seat member 31.
(5) In (4), the valve body housing 34 is formed of a member different from the suction valve seat member 31, and the 2 nd guide portion 34B1 is formed of the valve body housing 34.
(6) In (2), the outer diameter Φ30c of the protruding portion 30C is smaller than the outermost diameter Φ30a of the valve body 30A.
(7) In (3), the 2 nd guide portion 34B1 is formed in the pump body 1 for mounting the electromagnetic suction valve mechanism 300.
(8) In (1), the electromagnetic suction valve mechanism 300 includes the armature 36 and the core 39 that generate magnetic attraction force to each other, the armature 36 contacts the stem 30B when the valve is opened, the armature 39 separates from the stem 30B when the valve is closed, and a gap g3 is generated between the contact portions 36B, 30B2 of the armature 36 and the stem 30B when the valve is opened.
(9) The electromagnetic intake valve mechanism 300 includes an armature 36, a core 39, an intake valve 30, and an intake valve seat member 31, wherein the intake valve 30 is fixed so that a valve body 30A and a stem 30B extending from the valve body 30A to the armature 36 side always integrally operate, and the valve body 30A is abutted against the intake valve seat member 31 to seal fuel, and the intake valve 30 includes a1 st guide portion 31B guiding an outer peripheral portion 30B1 of the stem 30B and a2 nd guide portion 34B1 guiding an outer peripheral portion of the valve body 30A.
In the embodiment of the present invention, by integrally configuring the valve body 30A and the stem 30B and supporting both ends of the valve seat 30A1 of the suction valve 30, the inclination of the suction valve 30 at the time of opening and closing the valve of the suction valve 30 can be limited to be small. As a result, the corners of the suction valve 30 and the suction valve seat 30A1 contact the valve seat portion 31a of the suction valve seat member 31, and the possibility of damaging the valve seat portion 31a and reducing the oil tightness can be suppressed to a low level.
According to the present invention, by reducing the inclination of the intake valve 30 in the electromagnetic intake valve mechanism 300, it is possible to suppress a decrease in oil tightness, and it is possible to provide the high-pressure fuel pump 100 in which the cost is reduced by reducing the number of constituent parts.
Description of the reference numerals
30 … suction valve, 30a … valve body, 30B … stem, 30B1 … stem 30B outer peripheral portion, 30C … boss, 31 … suction valve seat member, 31B … 1 st guide portion, 34 … valve stopper (valve body housing portion), 34B1 … 2 nd guide portion, 36 … armature, 39 … core, 100 … high pressure fuel pump, 300 … electromagnetic suction valve mechanism.
Claims (8)
1. A high pressure fuel pump, characterized by:
comprising an electromagnetic suction valve mechanism with a suction valve,
the suction valve includes:
a stem portion;
a valve body integrally formed with the stem;
a1 st guide portion for guiding an outer peripheral portion of the lever portion; and
a2 nd guide part for guiding the outer periphery of the valve body part,
the 2 nd guide portion guides an outer periphery of a convex portion formed on a distal end side of the valve body portion.
2. The high pressure fuel pump of claim 1, wherein:
the 1 st guide portion is configured coaxially with the 2 nd guide portion.
3. The high-pressure fuel pump according to claim 2, characterized in that:
the high-pressure fuel pump includes a suction valve seat member on which the valve body is seated,
the 1 st guide portion is constituted by the suction valve seat member.
4. A high pressure fuel pump as claimed in claim 3, wherein:
the high-pressure fuel pump includes a valve body housing portion formed of a member different from the suction valve seat member,
the 2 nd guide portion is constituted by the valve body housing portion.
5. The high pressure fuel pump of claim 1, wherein:
the outer diameter of the protrusion is smaller than the outermost diameter of the valve body.
6. The high-pressure fuel pump according to claim 2, characterized in that:
the 2 nd guide portion is formed on a pump body for mounting the electromagnetic suction valve mechanism.
7. The high pressure fuel pump of claim 1, wherein:
the electromagnetic suction valve mechanism comprises an armature and a magnetic core which mutually generate magnetic attraction force,
the armature is in contact with the stem when the valve is opened, and the armature is separated from the stem when the valve is closed, thereby generating a gap between the armature and the stem.
8. A high pressure fuel pump, characterized by:
comprises an electromagnetic suction valve mechanism, wherein the electromagnetic suction valve mechanism is provided with an armature, a magnetic core, a suction valve and a suction valve seat component,
the suction valve is fixed in such a manner that a valve body portion and a stem portion extending from the valve body portion to the armature side always integrally operate, wherein the valve body portion is abutted against the suction valve seat member to seal fuel,
the suction valve includes:
a1 st guide portion for guiding an outer peripheral portion of the lever portion; and
a2 nd guide part for guiding the outer periphery of the valve body part,
the 2 nd guide portion guides an outer periphery of a convex portion formed on a distal end side of the valve body portion.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2019-079054 | 2019-04-18 | ||
| JP2019079054 | 2019-04-18 | ||
| PCT/JP2020/004725 WO2020213234A1 (en) | 2019-04-18 | 2020-02-07 | High-pressure fuel pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113692487A CN113692487A (en) | 2021-11-23 |
| CN113692487B true CN113692487B (en) | 2023-09-05 |
Family
ID=72838186
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202080028729.3A Active CN113692487B (en) | 2019-04-18 | 2020-02-07 | High-pressure fuel pump |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP7169438B2 (en) |
| CN (1) | CN113692487B (en) |
| DE (1) | DE112020001266T5 (en) |
| WO (1) | WO2020213234A1 (en) |
Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0194431A1 (en) * | 1985-02-08 | 1986-09-17 | M.A.N. - B&W Diesel GmbH | High-pressure fuel injection device for a combustion engine |
| US5156341A (en) * | 1988-06-08 | 1992-10-20 | Hitachi, Ltd. | Electromagnetic type fuel injection valve |
| CN101294530A (en) * | 2007-04-23 | 2008-10-29 | C.R.F.索奇埃塔·孔索尔蒂莱·佩尔·阿齐奥尼 | Fuel injector with balanced metering servovalve for an internal combustion engine |
| JP2012082849A (en) * | 2010-10-07 | 2012-04-26 | Hitachi Automotive Systems Ltd | Electromagnetic drive mechanism, solenoid valve using the electromagnetic drive mechanism and variable flow rate high-pressure fuel supply pump having solenoid inlet valve using the solenoid valve |
| CN102454523A (en) * | 2010-10-15 | 2012-05-16 | 日立汽车系统株式会社 | High-pressure fuel supply pump having electromagnetically-driven intake valve |
| CN102753812A (en) * | 2010-03-03 | 2012-10-24 | 日立汽车系统株式会社 | Electromagnetic flow control valve and high pressure fuel supply pump using same |
| JP2014141896A (en) * | 2013-01-22 | 2014-08-07 | Denso Corp | High pressure pump |
| KR20150065089A (en) * | 2013-12-04 | 2015-06-12 | 주식회사 현대케피코 | Valve for Flow Control |
| CN105587452A (en) * | 2016-02-05 | 2016-05-18 | 成都威特电喷有限责任公司 | Electric unit pump with two-channel low-pressure oil internal circulation oil path |
| JP2016094913A (en) * | 2014-11-17 | 2016-05-26 | 日立オートモティブシステムズ株式会社 | High-pressure fuel supply pump |
| CN106089661A (en) * | 2016-08-11 | 2016-11-09 | 山东博世机械有限公司 | A kind of tool is from the booster pump of voltage regulation performance |
| CN106795846A (en) * | 2014-08-28 | 2017-05-31 | 日立汽车系统株式会社 | High-pressure fuel feed pump |
| DE102015223965A1 (en) * | 2015-12-02 | 2017-06-08 | Robert Bosch Gmbh | Fuel injection system |
| CN109196217A (en) * | 2016-05-25 | 2019-01-11 | 日立汽车系统株式会社 | Fuel injection valve |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006061558A1 (en) | 2006-12-27 | 2008-07-03 | Robert Bosch Gmbh | Fuel delivery device for internal combustion engine of motor vehicle, has adjustable throttle device arranged upstream to suction valve, where outlet of throttle device is arranged directly proximate to suction valve |
| JP6533454B2 (en) | 2015-11-27 | 2019-06-19 | 日立オートモティブシステムズ株式会社 | High pressure fuel supply pump |
-
2020
- 2020-02-07 JP JP2021514803A patent/JP7169438B2/en active Active
- 2020-02-07 WO PCT/JP2020/004725 patent/WO2020213234A1/en active Application Filing
- 2020-02-07 DE DE112020001266.2T patent/DE112020001266T5/en active Pending
- 2020-02-07 CN CN202080028729.3A patent/CN113692487B/en active Active
Patent Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0194431A1 (en) * | 1985-02-08 | 1986-09-17 | M.A.N. - B&W Diesel GmbH | High-pressure fuel injection device for a combustion engine |
| US5156341A (en) * | 1988-06-08 | 1992-10-20 | Hitachi, Ltd. | Electromagnetic type fuel injection valve |
| CN101294530A (en) * | 2007-04-23 | 2008-10-29 | C.R.F.索奇埃塔·孔索尔蒂莱·佩尔·阿齐奥尼 | Fuel injector with balanced metering servovalve for an internal combustion engine |
| CN102753812A (en) * | 2010-03-03 | 2012-10-24 | 日立汽车系统株式会社 | Electromagnetic flow control valve and high pressure fuel supply pump using same |
| JP2012082849A (en) * | 2010-10-07 | 2012-04-26 | Hitachi Automotive Systems Ltd | Electromagnetic drive mechanism, solenoid valve using the electromagnetic drive mechanism and variable flow rate high-pressure fuel supply pump having solenoid inlet valve using the solenoid valve |
| CN102454523A (en) * | 2010-10-15 | 2012-05-16 | 日立汽车系统株式会社 | High-pressure fuel supply pump having electromagnetically-driven intake valve |
| JP2014141896A (en) * | 2013-01-22 | 2014-08-07 | Denso Corp | High pressure pump |
| KR20150065089A (en) * | 2013-12-04 | 2015-06-12 | 주식회사 현대케피코 | Valve for Flow Control |
| CN106795846A (en) * | 2014-08-28 | 2017-05-31 | 日立汽车系统株式会社 | High-pressure fuel feed pump |
| JP2016094913A (en) * | 2014-11-17 | 2016-05-26 | 日立オートモティブシステムズ株式会社 | High-pressure fuel supply pump |
| DE102015223965A1 (en) * | 2015-12-02 | 2017-06-08 | Robert Bosch Gmbh | Fuel injection system |
| CN105587452A (en) * | 2016-02-05 | 2016-05-18 | 成都威特电喷有限责任公司 | Electric unit pump with two-channel low-pressure oil internal circulation oil path |
| CN109196217A (en) * | 2016-05-25 | 2019-01-11 | 日立汽车系统株式会社 | Fuel injection valve |
| CN106089661A (en) * | 2016-08-11 | 2016-11-09 | 山东博世机械有限公司 | A kind of tool is from the booster pump of voltage regulation performance |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2020213234A1 (en) | 2020-10-22 |
| CN113692487A (en) | 2021-11-23 |
| WO2020213234A1 (en) | 2020-10-22 |
| DE112020001266T5 (en) | 2021-11-25 |
| JP7169438B2 (en) | 2022-11-10 |
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