Patent Application
20190277236
This application is based on Japanese Patent Application No. 2018-42226 filed on Mar. 8, 2018, the disclosure of which is incorporated herein by reference.
The present disclosure relates to a fuel injection valve and a fuel injection system.
A fuel injection valve is widely used for injecting fuel for causing combustion in an internal combustion engine. The fuel injection valve includes a valve element and a nozzle body. The valve element opens and closes a fuel passage by being unseated from and seated on a valve seat of the nozzle body.
According to an aspect of the present disclosure, a fuel injection valve includes an injection hole body, which has an injection hole to inject fuel for causing combustion in an internal combustion engine, and a valve body configured to be unseated from and seated on a seating surface of the injection hole body. The seating surface defines a seat angle in its cross section.
The above and other objects, features and advantages of the present invention will become more apparent from the following detailed description made with reference to the accompanying drawings. In the drawings:
According to an example of the present disclosure, a fuel injection valve is provided for injecting fuel from its injection holes for causing combustion in an internal combustion engine. The fuel injection valve includes an injection hole body, in which injection holes are formed, a valve body, and a resilient member. The valve body forms a fuel passage between the valve body and an inner surface of the injection hole body to communicate with the injection holes. The valve body opens and closes the fuel passage by being unseated from and seated on a seating surface of the injection hole body. The resilient member generates a resilient force to urge the valve body onto the seating surface.
According to the example of the present disclosure, in a state where the valve body is seated on the seating surface, pressure (supply fuel pressure) of fuel supplied into the fuel injection valve could act in a direction in which the valve body is urged against the seating surface. The force caused by the fuel pressure and acting on the valve body is referred to as a fuel pressure valve closing force. In addition, the above-mentioned resilient force of the resilient member is referred to as a resilient valve closing force. In view of the present technical trend, it would be considered that the fuel pressure has been increasing, and the fuel pressure valve closing force has been increasing. According to this view point, the force (required valve opening force), which is required to unseat the valve body from the seating surface, is considered to be becoming large. Therefore, in order to suppress the increase in the required valve opening force, the resilient valve closing force may be reduced.
However, even in a case where a fuel injection valve is configured to inject high-pressure fuel at, for example, about 100 MPa, the fuel injection valve may inject fuel at, for example, about 40 MPa in a specific case. Therefore, the supplied fuel pressure is considered to have a range between its maximum pressure and its minimum pressure. The required valve opening force is considered to become the highest at the maximum pressure. Therefore, the resilient valve closing force may be set in consideration of the maximum pressure. However, in a case where the resilient closing force is set in this manner and in a case of the minimum pressure, the resilient closing valve force is considered to decrease, and the fuel pressure valve closing force may also decreases. Therefore, the valve closing force applied to the valve body could decrease. As a result, a phenomenon of bouncing could be likely to occur. Specifically, the valve body, which performs a valve closing operation, comes into contact (collide) with the seating surface, and immediately after, the valve body could be likely to be bounced back and seated.
According to an aspect of the present disclosure, a fuel injection valve comprises an injection hole body having an injection hole to inject fuel for causing combustion in an internal combustion engine. The a fuel injection valve further comprises a valve body configured to be unseated from and seated on a seating surface of the injection hole body. The injection hole body and the valve body are configured to form a fuel passage therebetween to communicate with an inflow port of the injection hole. The fuel passage is opened and closed by unseating and seating of the valve body. The fuel injection valve further comprises a resilient member configured to generate a resilient force to urge the valve body toward the seating surface. A seat angle is an angle between two straight lines appearing in a cross section of the seating surface, the cross section including a center axis of the valve body. The seat angle is 90 degrees or less.
As follows, the valve body is assumed to be a mass point that collides with the seating surface when the valve body performing a valve closing operation collides with the seating surface and bounces. Subsequently, a momentum about this mass point will be described below. The momentum of the mass point immediately before the bouncing (pre-collision momentum) is a value obtained by multiplying a mass point velocity immediately before bounding by a mass of the mass point. A moving direction of the mass point having the pre-collision momentum is the direction toward the seating surface along the direction of the center axis. The momentum of the mass point immediately after the bouncing (post-collision momentum) is a value obtained by multiplying a mass point velocity immediately after bounding by the mass of the mass point. A moving direction of the mass point having the post-collision momentum is a reflection direction, which will be described as follows. More specifically, a collision angle of the mass point relative to the seating surface corresponds to an incident angle. The incident angle is an angle between a line, which extends along the moving direction of the mass point having the pre-collision momentum, and a line perpendicular to the seating surface. More specifically, a collision angle of the mass point relative to the seating surface corresponds to an incident angle. The incident angle is an angle between a line, which extends along the moving direction of the mass point having the pre-collision momentum, and a line perpendicular to the seating surface.
The incident angle is the same as the reflection angle. The moving direction of the mass point having the pre-collision momentum is specified to the direction of the center axis. Therefore, the reflection angle is also specified by specifying the seat angle and by specifying the angle of the seating surface. Thus, the moving direction of the mass point having the momentum after collision is also specified. Based on this finding, in a case where the seat angle is 90 degrees, the moving direction of the mass point having the post-collision momentum is a direction perpendicular to the center axis (hereinafter referred to as a horizontal direction). In a case where the seat angle is larger than 90 degrees, the moving direction of the mass point, which has the post-collision momentum, is upward (in the direction of the valve opening) with respect to the horizontal direction. In a case where the seat angle is smaller than 90 degrees, the moving direction of the mass point, which has the post-collision momentum, is downward (in the direction of the valve closing) with respect to the horizontal direction.
Focusing on this issue, according to the aspect, the seat angle is set to 90 degrees or less. For that reason, the configuration enables to restrict the valve body colliding with the seating surface from bouncing toward the valve opening side. Therefore, the bouncing of the valve body can be reduced.
A fuel injection system according to another aspect includes the fuel injection valve of the aspect and a control device configured to control a fuel injection state from the injection holes by controlling the state in which the valve body is unseated from and seated on the seating surface. The configuration enables to produce similar advantages to those of the aspect.
Hereinafter, multiple embodiments of the present disclosure will be described with reference to the drawings. The same reference numerals are assigned to the corresponding elements in each embodiment, and thus, duplicate descriptions may be omitted. In a case where only a part of the configuration is described in an embodiment, the configuration of another embodiment described above may be applied to other parts of the configuration.
A fuel injection valve 1 shown in
The fuel injection valve 1 is of a center placement type placed at a center of the combustion chamber 2. More specifically, the injection holes 11a are located between an intake port and an exhaust port when viewed along an axis line direction of a piston of the internal combustion engine. The fuel injection valve 1 is mounted to the cylinder head so that the axis line direction of the fuel injection valve 1, which corresponds to a vertical direction in
The operation of the fuel injection valve 1 is controlled by a control device 90 mounted on the vehicle. The control device 90 has at least one arithmetic processing device (processor) 90a and at least one storage device (memory) 90b as a storage medium for storing a program executed by the processor 90a and data. The fuel injection valve 1 and the control device 90 configure a fuel injection system.
The processor 90a and the memory 90b may be provided as a microcomputer. The storage medium is a non-transitory tangible storage medium that non-transitorily stores programs readable by the processor 90a. The storage medium may be provided as a semiconductor memory, a magnetic disk, or the like. The control device 90 may be provided as a computer or a set of computer resources linked via a data communication device. The program is executed by the control device 90 to cause the control device 90 to function as a device described in the present specification and to cause the control device 90 to function to perform the methods described in the present specification.
The fuel injection valve 1 includes an injection hole body 11, a main body 12, a stationary core 13, a nonmagnetic member 14, a coil 17, a support member 18, a filter 19, a first spring member SP1 (resilient member), a cup 50, a guide member 60, a movable portion M (refer to
As shown in
A seating surface 11s is formed by an inner peripheral surface of the injection hole body 11. A seat surface 20s formed on the needle 20 is unseated from and seated onto the seating surface 11s. The seat surface 20s and the seating surface 11s are shaped to extend annularly around a center axis (axis line C1) of the needle 20. When the needle 20 is unseated from and seated onto the seating surface 11s, the fuel passage 11b is opened and closed, and the injection hole 11a is opened and closed. Specifically, when the needle 20 makes contact with and seats on the seating surface 11s, the fuel passage 11b and the injection hole 11a do not communicate with each other. When the needle 20 moves away from the seating surface 11s and is unseated, the fuel passage 11b and the injection hole 11a communicate with each other. At this time, the fuel is injected from the injection hole 11a.
When the needle 20 is operated to perform a valve closing operation and to cause the seat surface 20s to come into contact with the seating surface 11s, the seat surface 20s and the seating surface 11s come into line contact with each other at a seat position R1 indicated by a one-dot chain line in
Referring back to the illustration of
A nut member 15 is fastened to a threaded portion 13N of the stationary core 13 in a state of being engaged with a locking portion 12c of the main body 12. An axial force caused by the above engagement generates a surface pressure that causes the nut member 15, the main body 12, the nonmagnetic member 14, and the stationary core 13 to be pressed against each other along the direction of the axis line C1, that is, in the vertical direction in
The main body 12 is made of a magnetic material such as stainless steel. The main body 12 has a flow channel 12b for allowing the fuel to flow toward the injection hole 11a. The needle 20 is accommodated in the flow channel 12b and movable in the direction of the axis line C1. A movable portion M (refer to
The flow channel 12b communicates with a downstream side of the movable chamber 12a and extends along the direction of the axis line C1. The center line of the flow channel 12b and the movable chamber 12a coincides with the cylinder center line(axis line C1) of the main body 12. An injection hole side portion of the needle 20 is slidably supported by an inner wall surface 11c of the injection hole body 11. A portion of the needle 20 opposite to the injection hole is slidably supported by the inner wall surface of the cup 50. The two positions of the upstream end portion and the downstream end portion of the needle 20 are slidably supported in this manner. In this way, the movement of the needle 20 in the radial direction is limited, and an inclination of the needle 20 with respect to the axis line C1 of the main body 12 is also limited.
The needle 20 corresponds to a valve body that opens and closes the injection hole 11a by opening and closing the fuel passage 11b. The needle 20 is formed of a magnetic material, such as stainless steel, and is in a shape extending in the direction of the axis line C1. The above-described seat surface 20s is formed on an end face of the needle 20 on the downstream side. When the needle 20 moves toward the downstream side along the direction of the axis line C1 with the valve closing operation, the seat surface 20s is seated on the seating surface 11s, and the fuel passage 11b and the injection hole 11a are closed. When the needle 20 moves toward the upstream side along the direction of the axis line C1 with a valve opening operation, the seat surface 20s is unseated from the seating surface 11s, and the fuel passage 11b and the injection hole 11a are opened.
The cup 50 has a disc portion 52 in a shape of a disk and a cylindrical portion 51 in a shape of a cylinder. The disc portion 52 has a through hole 52a extending along the direction of the axis line C1. A surface of the disc portion 52 on the opposite side of the injection hole functions as a spring abutment surface 52b that is in contact with the first spring member SP1. A surface of the disc portion 52 on the injection hole side functions as a valve closing force transmission abutment surface 52cthat makes contact with the needle 20 and transmits a first resilient force (valve closing resilient force). The cylindrical portion 51 is in a cylindrical shape extending from an outer peripheral end of the disc portion 52 toward the injection hole. The injection hole side end face of the cylindrical portion 51 functions as a core contact end surface 51a that makes contact with the movable core 30. An inner wall surface of the cylindrical portion 51 slides with an outer peripheral surface of an abutment portion 21 of the needle 20.
The stationary core 13 is made of a magnetic material, such as stainless steel, and has a flow channel 13a for allowing the fuel to flow toward the injection hole 11a. The flow channel 13a communicates with an internal passage 20a formed inside the needle 20 (refer to
The support member 18 is in a cylindrical shape and is press-fitted and fixed to the inner wall surface of the stationary core 13. The first spring member SP1 is a coil spring located on the downstream side of the support member 18. The first spring member SP1 is resiliently deformed in the direction of the axis line C1. An upstream side end face of the first spring member SP1 is supported by the support member 18. A downstream side end face of the first spring member SP1 is supported by the cup 50. The cup 50 is urged toward the downstream side by a force (first resilient force) caused by a resilient deformation of the first spring member SP1. With adjustment of the amount of press-fit of the support member 18 in the direction of the axis line C1, a magnitude of the resilient force for urging the cup 50 (a first set load) is adjusted.
The filter 19 is in a mesh shape and captures foreign matter contained in the fuel supplied to the fuel injection valve 1. The filter 19 is held by a holding member 19a. The holding member 19a is press-fitted to and fixed with an upstream side portion of the support member 18 in the inner wall surface of the stationary core 13. The filter 19 is in a cylindrical shape. As indicated by an arrow Y1 in
As shown in
A resin member 16 is provided on an outer peripheral surface of the stationary core 13. The resin member 16 has a connector housing 16a. A terminal 16b is accommodated in the connector housing 16a. The terminal 16b is electrically connected to the coil 17. An external connector (not shown) is connected to the connector housing 16a. An electric power is supplied to the coil 17 through the terminal 16b. The coil 17 is wound around a bobbin 17a having an electrical insulation property and is in a cylindrical shape. The coil 17 is located on a radially outer side of the stationary core 13, the nonmagnetic member 14, and the movable core 30. As shown by a dotted arrow in
As shown in
The needle 20 is inserted into a cylindrical inner portion of the inner core 32. The inner core 32 is assembled to the needle 20 so as to be slidable with respect to the needle 20 along the direction of the axis line C1. The inner core 32 makes contact with the guide member 60 as a stopper member, the cup 50, and the needle 20. For that reason, a material having a higher hardness than that of the outer core 31 is used for the inner core 32. The outer core 31 has a core facing surface 31c facing the stationary core 13. A gap is formed between the core facing surface 31c and the stationary core 13. Therefore, in a state in which the magnetic flux flows in the coil 17 with energization as described above, a magnetic attraction force toward the stationary core 13 acts on the outer core 31 through the gap.
The sleeve 40 is press-fitted to and fixed with the needle 20 and supports an injection hole side end face of the second spring member SP2. The second spring member SP2 is a coil spring located on the side of a support portion 43 opposite to the injection holes. The second spring member SP2 is resiliently deformed in the direction of the axis line C1. An end face of the second spring member SP2 opposite to the injection holes is supported by the outer core 31. An injection hole side end face of the second spring member SP2 is supported by the support portion 43. The outer core 31 is urged toward the opposite side of the injection holes by a force (second resilient force) caused by the resilient deformation of the second spring member SP2. With adjustment of the amount of press-fit of the sleeve 40 along the direction of the axis line C1, a magnitude of the second resilient force urging the movable core 30 (a second set load) at the time of the valve closing is adjusted. The second set load of the second spring member SP2 is smaller than the first set load of the first spring member SP1.
(Description of Operation)
Subsequently, the operation of the fuel injection valve 1 will be described with reference to
First, an outline of the operation of the fuel injection valve 1 will be described. On generation of the magnetic attraction force by energizing the coil 17 to attract the movable core 30, the movable core 30 makes contact with the needle 20 when the movable core 30 is moved by a predetermined amount toward the opposite side of the injection holes, thereby to activate the needle 20 to perform the valve opening operation. That is, after the movable core 30 has moved by the predetermined amount, the needle 20 starts the valve opening operation. When the energization of the coil 17 is turned off, the cup 50 makes contact with the needle 20 when the cup 50 is moved toward the injection hole side together with the movable core 30, thereby to cause the needle 20 to perform the valve closing operation. That is, after the cup 50 and the movable core 30 have moved by the predetermined amount, the needle 20 starts the valve closing operation. In short, the fuel injection valve 1 is of a direct acting type including the movable core 30 and the needle 20. The movable core 30 is attracted and moved by the magnetic force generated by the energization, and the needle 20 moves together with the movable core 30 to be unseated from the seating surface 11s thereby to perform the valve opening operation.
Subsequently, the operation of the fuel injection valve 1 will be described in detail. As shown by (a) in
The movable core 30 is urged toward the valve closing side by the first resilient force of the first spring member SP1 transmitted from the cup 50. In addition, the movable core 30 is also urged toward the valve opening side by the second resilient force of the second spring member SP2. Since the first resilient force is larger than the second resilient force, the movable core 30 is biased by the cup 50 and is moved (lifted down) toward the injection holes. The needle 20 is urged toward the valve closing side by the first resilient force transmitted from the cup 50. Thus, the needle 20 is biased by the cup 50 to move (lift down) toward the injection hole side. That is, the needle 20 is seated on the seating surface 11s to be in the valve closed state. In the valve closed state, a gap is formed between a valve-opening-state valve body abutment surface 21a (refer to
As shown by (b) in
After the collision, the movable core 30 continues to move further by application of the magnetic attraction force. When the movement amount after the collision reaches the lift amount L2, the inner core 32 collides with the guide member 60 and stops moving as shown by (c) in
The above-described operation will be further described in detail with reference to (a) to (c) in
Thereafter, at a time point t3 when the moving amount of the movable core 30 reaches the gap amount L1, the movable core 30 collides with the needle 20, and the needle 20 starts the valve opening operation. As a result, fuel is injected from the injection holes 11a. Thereafter, the movable core 30 lifts up the needle 20 against the valve closing resilient force. At a time point t4 when the movable core 30 collides with the guide member 60, the lift amount of the needle 20 reaches the full lift amount L2. Thereafter, the full lift state of the needle 20 is maintained by the magnetic attraction force. Thus, the fuel injection is continued. Thereafter, when the energization is switched OFF at a time point t5, the magnetic attraction force also decreases with decrease in the drive current. At a time point t6 when the magnetic attraction force reaches the actual valve closing resilient force F0, the movable core 30 starts moving toward the valve closing side together with the cup 50. The needle 20 is biased against pressure of the fuel filled between and the needle 20 and the cup 50 to initiate a lift-down (valve closing operation) as soon as the cup 50 begins to move.
Thereafter, at a time point t7 when the needle 20 is lifted down by the lift amount L2, the seat surface 20s is seated on the seating surface 11s. Thus, the fuel passage 11b and the injection hole 11a are closed. Thereafter, the movable core 30 continues to move toward the valve closing side together with the cup 50. The movement of the cup 50 toward the valve closing side is stopped at a time point t8 when the cup 50 makes contact with the needle 20. Thereafter, the movable core 30 further continues to move toward the valve closing side (inertial movement) by an inertial force. Thereafter, the movable core 30 moves (rebounds) toward the valve opening side by the resilient force of the second spring member SP2. Thereafter, the movable core 30 collides with the cup 50 at a time point t9 and moves (rebound) toward the valve opening side together with the cup 50. However, the movable core 30 is immediately biased back by the valve closing resilient force to converge to the initial state shown by (a) in
In consideration of that, the smaller the rebound is, the shorter a time required for convergence is, and the shorter a time from the end of injection to the return to the initial state is. For that reason, in the multi-stage injection to inject the fuel for a plurality of times per combustion cycle of the internal combustion engine, an interval between the injections can be shortened. Thus, the number of injections in the multi-stage injection can be increased.
The above-described energization ON/OFF is controlled by the processor 90a executing the program stored in the memory 90b. Fundamentally, a fuel injection amount, an injection timing, and the number of injections relating to the multi-stage injection in one combustion cycle are calculated by the processor 90a based on a load and a rotation speed of the internal combustion engine. Further, the processor 90a executes various programs to perform a multi-stage injection control, a partial lift injection control (PL injection control), a compression stroke injection control, and a pressure control, which will be described below. The control device 90 when executing those controls corresponds to a multi-stage injection control unit 91, a partial lift injection control unit (PL injection control unit) 92, a compression stroke injection control unit 93, and a pressure control unit 94 shown in
The multi-stage injection control unit 91 controls the energization ON/OFF of the coil 17 so as to inject the fuel from the injection holes 11a for multiple times in one combustion cycle of the internal combustion engine. The PL injection control unit 92 controls the energizing ON/OFF of the coil 17 such that after the needle 20 has been unseated from the seating surface 11s, the needle 20 starts the valve closing operation before reaching a maximum valve opening position. For example, as the number of the multi-stage injections increases, the injection amount of one injection becomes very small. Therefore, in the case of such a small amount of injection, the PL injection control is executed.
The compression stroke injection control unit 93 controls the energization ON/OFF of the coil 17 so as to inject the fuel from the injection holes 11a in a period including a part of a compression stroke period of the internal combustion engine. When the fuel is injected into the combustion chamber 2 in the compression stroke period, a time from an injection start timing to an ignition timing is short. Therefore, a time for sufficiently mixing the fuel and an air is short. For that reason, the fuel injection valve 1 of this type is required to inject the fuel from the injection holes 11a with a high penetration force in order to promote mixing of the fuel and the air. In addition, an injection pressure is required to increase in order to divide spray in a short time.
The pressure control unit 94 controls the pressure (fuel supply pressure) of the fuel to be supplied to the fuel injection valve 1 to any target pressure within a predetermined range. Specifically, the pressure control unit 94 controls the fuel supply pressure by controlling a fuel discharge amount from the fuel pump described above. A force, by which the needle 20 is pressed on the seating surface 11s, is a minimum fuel pressure valve closing force caused by the fuel pressure when a target pressure is set to a minimum value in a predetermined range. The first resilient force (valve closing resilient force) caused by the first spring member SP1 is set to be smaller than the minimum fuel pressure valve closing force.
(Detailed Description of Fuel Passage 11b)
Hereinafter, the fuel passage 11b will be described in detail with reference to
Multiple injection holes 11a are formed. The inflow ports 11in of the multiple injection holes 11a are placed at equal intervals on a virtual circle (inflow central virtual circle R2) centered on the axis line C1. The outflow ports 11out of the multiple injection holes 11a are similarly placed at equal intervals around the axis line C1. In other words, both of the inflow ports 11in and the outflow ports 11out are placed at equal intervals on a concentric circle. The shapes and sizes of the multiple injection holes 11a are all the same. Specifically, each of the injection holes 11a is in a straight shape, in which a shape of the passage cross section is a perfect circle and in which a diameter of the perfect circle does not change from the inflow port 11in to the outflow port 11out. The passage cross section referred to in the present description is a cross-section taken perpendicularly to an axis line C2 passing through the center of each injection hole 11a.
As shown in
As shown in
The inter-injection hole distance L defined as the length between the injection holes along the inflow central virtual circle R2 is smaller than the inflow port gap distance H. In addition to that, a second inter-injection hole distance described below is also smaller than the inflow port gap distance H.
The second inter-injection hole distance is defined as a shortest straight line length between the outer peripheral edges of the inflow ports 11in adjacent to each other.
The inter-injection hole distance L is smaller than the inflow port gap distance H defined as the needle separation distance Ha at the position indicated by the reference numeral A1. In addition to that, the inter-injection hole distance L is smaller than a second inflow port gap distance. The second inflow port gap distance will be described below. The second inflow port gap distance is defined as the needle separation distance Ha at the inflow port center point A. Further, the second inter-injection hole distance is set to be smaller than the second inflow port gap distance.
The inter-injection hole distance L is smaller than the inflow port gap distance H. More specifically, the inter-injection hole distance L is smaller than the inflow port gap distance H in a state in which the needle 20 is unseated from the seating surface 11s and is at the position farthest from the seating surface 11s, that is, the needle 20 is in a maximum valve open position (full lift position). The maximum valve open position is a position of the needle 20 in the direction of the axis line C1 in a state where the inner core 32 is in contact with the stopper abutment end face 61a and where the valve-opening-state valve body abutment surface 21a is in contact with the inner core 32.
Further, the inter-injection hole distance L is smaller than the inflow port gap distance H in the state in which the needle 20 is seated on the seating surface 11s, that is, in the valve closed state. The inflow port gap distance H in the closed state is larger than the mesh interval Lm of the filter 19. As shown in
In the fuel passage 11b formed between the inner surface of the injection hole body 11 and the outer surface of the needle 20, a seat upstream passage Q10 is a portion on the upstream side of the seating surface 11s and the seat surface 20s, and a seat downstream passage Q20 is a portion on the downstream side of the seating surface 11s and the seat surface 20s. The seat downstream passage Q20 has a tapered chamber Q21 and the sac chamber Q22.
As shown in
The body bottom surface 112 is a portion of the inner surface of the injection hole body 11 including the axis line C1 and forming the sac chamber Q22. The coupling surface 113 is a portion of the inner surface of the injection hole body 11 connecting the body bottom surface 112 with the tapered surface 111. The coupling surface 113 is in a linear shape and is in a shape extending in a direction intersecting with the axis line C1 in the cross section including the axis line C1. The coupling surface 113 is in an annular shape when viewed along the direction of the axis line C1 (refer to
The valve body tip end face 22 is a surface in the outer surface of the needle 20 including the seat surface 20s and a portion on the downstream side of the seat surface 20s. The needle separation distance Ha is the distance between the valve body tip end face 22 and the injection hole body 11 in the direction in which the needle 20 is unseated and seated, specifically, is the distance between the body bottom surface 112 and the valve body tip end face 22 in the direction of the axis line C1.
The valve body tip end face 22 is in a shape curved in a direction to swell toward the side of the body bottom surface 112. A radius of curvature R22 of the valve body tip end face 22 (refer to
The body bottom surface 112 is in a shape curved and concaved in a direction toward the valve body tip end face 22, that is, the body bottom surface 112 is in a shape curved in the same direction as that of the valve body tip end face 22. A radius of curvature R112 of the body bottom surface 112 (refer to
In a body outer surface 114 which is an outer surface of the injection hole body 11, an outer surface center region 114a is a region of a portion closer to the axis line C1 in the radial direction than the outflow port 11out (refer to
A surface roughness of a portion of the injection hole body 11 which forms the fuel passage 11b is rougher than a surface roughness of portions of the injection hole body 11 which forms the injection holes 11a. More specifically, the surface roughness of the body bottom surface 112 is rougher than the surface roughness of the inner wall surfaces of the injection holes 11a. The injection holes 11a are formed by laser machining. To the contrary, the inner surface of the injection hole body 11 is formed by cutting.
A virtual circle is in contact with portions of the peripheral edges of the multiple inflow ports 11in, which are closest to the axis line C1 in the radial direction. The virtual circle is centered on the axis line C1. A virtual cylinder is formed by extending the virtual circle straight from the body bottom surface 112 toward the valve body tip end face 22 along the direction of the axis line C1. A central cylindrical volume V1a is a volume of a portion of the fuel passage 11b surrounded by the virtual cylinder, the body bottom surface 112, and the valve body tip end face 22 (refer to
The virtual circle according to the present embodiment is a virtual inscribed circle R4 inscribed in the multiple inflow ports 11in. In addition, a seat downstream volume V3 is a volume of all portions of the fuel passage 11b on the downstream side of the seating surface 11s, that is, a volume of the seat downstream passage Q20 (refer to
A total injection hole volume V2 is a total of the volumes V2a of the multiple injection holes 11a. In the present embodiment, ten injection holes 11a are formed, and the volumes V2a of all the injection holes 11a are the same. Therefore, a value 10 times as large as the volume V2a of one injection hole 11a coincides with the total injection hole volume V2. The volume V2a of the injection hole 11a corresponds to a volume of the region between the inflow port 11in and the outflow port 11out of the injection hole 11a. The volume V2a of the injection hole 11a may be calculated from a tomographic image of the injection hole body 11 obtained by irradiating X-rays, for example. Similarly, other volumes defined in the present embodiment may be calculated from the tomographic image.
The total injection hole volume V2 is larger than the center volume V1 in the state in which the needle 20 is seated on the seating surface 11s and is larger than the center volume V1 in the state in which the needle 20 is farthest from the seating surface 11s (that is, in the full lift state). In addition, the total injection hole volume V2 is larger than the seat downstream volume V3 in the seated state and larger than the seat downstream volume V3 in the full lift state. Similarly to the center volume V1, the central cylindrical volume V1a is smaller than the total injection hole volume V2 in both of the full lift state and the seated state.
A dotted portion in
A total peripheral length L5 is a total of peripheral lengths L5a of the inflow ports 11in of the multiple injection holes 11a (refer to
A tangential direction of the valve body tip end face 22 at the seat position R1 is the same as a tangential direction of the tapered surface 111 at the seat position R1. The valve body tip end face 22 is in a curved shape in the cross section including the axis line C1. To the contrary, the tapered surface 111 is in a linear shape in the cross section including the axis line C1. A seat angle θ is an apex angle at an apex where extension lines of the tapered surface 111 intersect with each other (refer to
An area of a plane in the injection hole 11a, which is perpendicular to the axis line C2 of the injection hole 11a, is defined as a passage cross sectional area. A total of the passage cross sectional areas of the multiple injection holes 11a is defined as a total injection hole area. In the present embodiment, the shape of the injection hole 11a is the same regardless of the position in the direction of the axis line C2 to have the same cross-sectional area. In a case where the shape of the injection hole 11a is a shape to have a different passage cross-sectional area depending on the position in the direction of the axis line C2, a total of those minimum cross-sectional areas of the passages is defined as the total injection hole area.
Further, in a state where the needle 20 is at the position farthest from the seating surface 11s in the movable range of the needle 20, that is, where the needle 20 is in the full lift state, a cross sectional area of an annular passage on the seating surface 11s in the fuel passage 11b is defined as the seat annular area. The seat annular area is an area of a section, which is formed by elongating an imaginary line in an annular form about the axis C1. The imaginary line is a line between a point of the tapered surface 111, which passes through the seat position R1, and the valve body tip end face 22 and takes the shortest distance therebetween.
As the seat angle θ is increased with the seat diameter Ds maintained the same, the above-described imaginary line, which takes the shortest distance, becomes shorter, and the seat annular area becomes smaller. To the contrary, as the seat angle θ is decreased with the seat diameter Ds maintained the same, the above-described imaginary line, which takes the shortest distance, becomes longer, and the seat annular area becomes larger. The seat angle θ is set so that the seat annular area is larger than the total injection hole area.
(Operation Effect)
When the needle 20 performing the valve-closing operation collides with the seating surface 11s and bounces thereon, assuming that the needle 20 is a mass point colliding with the seating surface 11s, the seat angle θ may be described as below. When the seat angle θ is larger than 90 degrees, a moving direction of the mass point, which has a post-collision momentum, is upward (in the direction of the valve opening) with respect to the horizontal direction. When the seat angle θ is smaller than 90 degrees, the moving direction of the mass point, which has the post-collision momentum, is downward (in the direction of the valve closing) with respect to the horizontal direction. Focusing on this issue, in the present embodiment, the seat angle θ is set to 90 degrees or less. For that reason, the configuration enables to restrict the needle 20, which has collided with the seating surface 11s, from bouncing toward the valve opening side. Therefore, the bouncing of the needle 20 can be reduced.
Further, according to the present embodiment, the valve body tip end face 22 of the outer surface of the needle 20 is a surface including the seat position R1. The valve body tip end face 22 is curved in the direction to swell toward the body bottom surface 112. For that reason, when the needle 20 and the injection hole body 11 are resiliently deformed and come into surface contact with each other, the surface contact area of the valve body tip end face 22 can be increased, as compared to a case where tapered surfaces having different taper angles, respectively, are connected to each other at the seat position R1 to be in a non-curved shape. For that reason, according to the present embodiment, the configuration, in which the valve body tip end face 22 has the curved shape, enables to enhance a sealing property between the seat surface 20s and the seating surface 11s. Therefore, the configuration enables to reduce a possibility that the fuel leaks from the seat upstream passage Q10 to the seat downstream passage Q20 when the valve is closed.
Further, according to the present embodiment, the filter 19 that captures foreign matter contained in the fuel flowing into the fuel passage 11b is provided. The diameter of a portion of the injection hole 11a, at which its passage cross-sectional area is minimum, is larger than the mesh interval Lm of the filter 19. The passage cross-sectional area is an area of a cross section taken perpendicular to the axis line C2. According to the above configuration, the foreign matter that has passed through the filter 19 is likely smaller than the mesh interval Lm. The diameter of the injection hole 11a is larger than the mesh interval Lm, and therefore, a concern that the foreign matter would clog the injection hole 11a can be reduced.
Further, in the present embodiment, the total of the passage sectional areas of the multiple injection holes 11a is defined as the total injection hole area. The cross sectional area of the annular passage, which is located on the seating surface 11s in the fuel passage 11b when being in the full lift state, is defined as the seat annular area. As the seat angle θ becomes smaller, the seat annular area becomes larger as described above. The seat angle θ is set so that the seat annular area is larger than the total injection hole area. Therefore, in addition to the seat angle θ being 90 degrees or less, the seat angle θ is reduced so that the seat annular area is larger than the total injection hole area. The configuration enables to promote the bounce reduction of the needle 20. As described above, fuel in the seat downstream passage Q20 would flow out of the outflow port 11out by its inertia immediately after the valve closing, and subsequently, the fuel would leak out of the outflow port 11out by its own weight. Consequently, it is concerned that the leaking fuel would adhere to the body outer surface 114 and would accumulate as a deposit. In view of the above concern, by reducing the volume of the seat downstream passage Q20 to reduce the inflow port gap distance H, the amount of the fuel to be leaked can be reduced. Consequently, the leak amount can be reduced, so that deposit development can be reduced.
On the other hand, the flow directions of the fuel in the seat upstream passage Q10 and the fuel in the tapered chamber Q21 are largely different from the flow direction of the fuel in the injection holes 11a. Therefore, the flow direction of the fuel changes (bends) abruptly when the fuel flows from the sac chamber Q22 into the inflow ports 11in. Assuming that the inflow port gap distance H is reduced in order to reduce the leak amount, the abrupt change (bending) in the flow direction is promoted. Consequently, an increase in a pressure loss is promoted. In other words, a reduction in the inflow port gap distance H in order to reduce the fuel leakage amount causes a conflict to a reduction in the pressure loss.
In this example, as described above, the fuel that passes around the seat position R1 and flows into the seat downstream passage Q20 changes its fuel direction to the direction indicated by the arrow Y3 in
In both of the longitudinal inflow fuel Y3a and the lateral inflow fuel Y3b, the pressure loss increases as the inflow port gap distance H decreases in order to reduce the volume of the seat downstream passage Q20. As for the lateral inflow fuel Y3b, the increase in the pressure loss may be mitigated by reducing the inter-injection hole distance L. Therefore, an increase in the pressure loss due to the reduction in the inflow port gap distance H may be mitigated by reducing the inter-injection hole distance L.
The mitigation will be described in detail with reference to
A vector shown in a right column of the figure represents a flow velocity of the lateral inflow fuel Y3b as a vector. The flow velocity vector of the lateral inflow fuel Y3b may be decomposed into a lateral component Y3bx which is a component perpendicular to the axis line C1 and a longitudinal component Y3by which is a component parallel to the axis line C1. An inflow angle θ2 is an angle of the flow velocity vector of the lateral inflow fuel Y3b with respect to the axis line C1. The larger a ratio of the longitudinal component Y3by to the lateral component Y3bx is, the smaller the inflow angle θ2 is. As shown in the right column of
In the present embodiment focused on the above issues, as shown in
As described above, according to the present embodiment, the inter-injection hole distance L is smaller than the inflow port gap distance H. Therfore, the pressure loss of the lateral inflow fuel Y3b can be mitigated as compared with the case in which the inter-injection hole distance L is larger than the inflow port gap distance H. Therefore, the increase in the pressure loss caused by reducing the inflow port gap distance H can be mitigated while reducing the volume of the seat downstream passage Q20 by reducing the inflow port gap distance H. That is, the present embodiment enables to achieve both of the reduction in the fuel leakage amount by reducing the volume of the seat downstream passage Q20 and the reduction in the pressure loss by reducing the inter-injection hole distance L.
In addition, as the pressure loss is reduced as described above, the flow velocity of the fuel flowing from the sac chamber Q22 into the injection holes 11a increases. This configuration enables to restrict foreign matter contained in the fuel from staying in the sac chamber Q22 and to enhance a property for discharging foreign matter from the injection holes 11a. In addition, the residual fuel can be reduced by reducing the volume of the seat downstream passage Q20. Therefore, a property for discharging the residual fuel can be enhanced with the reduction in the pressure loss by reducing the inter-injection hole distance L.
Further, according to the present embodiment, the inter-injection hole distance L is smaller than the inflow port gap distance H in the state in which the needle 20 is seated on the seating surface 11s. For that reason, in the seated state, the inflow angle θ2 of the lateral inflow fuel Y3b becomes smaller than that in the case where the inter-injection hole distance L is larger than the inflow port gap distance H. Therefore, the effect of mitigating the increase in the pressure loss of the lateral inflow fuel Y3b can be promoted.
Further, according to the present embodiment, the virtual circle that is in contact with the portions of the peripheral edges of the multiple inflow ports 11in closest to the axis line C1 and that is centered on the axis line C1 is of the virtual cylinder that extends straight from the inflow port 11in toward the needle 20 along the direction of the axis line C1. The volume of the space surrounded by the virtual cylinder in the fuel passage 11b is defined as the center volume V1. The total volume of the multiple injection holes 11a is defined as the total injection hole volume V2. The total injection hole volume V2 is set to be larger than the center volume V1.
For that reason, a flow rate of the main flow can be increased as compared with the case where the total injection hole volume V2 is set to be smaller than the center volume V1. In addition, the amount of fuel that is hardly attracted to the main flow can be reduced as compared with the case where the total injection hole volume V2 is set to be smaller than the center volume V1. As a result, the configuration enables to reduce the residual fuel that cannot be jetted out of the injection holes 11a rapidly at a high flow velocity together with the main flow. Therefore, the fuel adhering to the outer body surface 114 and the inner surface of the injection hole 11a can be reduced. In addition, the deposit can be restricted from being developed on the body outer surface 114.
Further, according to the present embodiment, the total injection hole volume V2 is set to be larger than the center volume V1 in the state in which the needle 20 is unseated from the seating surface 11s and is at the position farthest away in the movable range of the needle 20, that is, the needle 20 is at the full lift position. For that reason, as compared with the case where the total injection hole volume V2 is set to be smaller than the center volume V1 in the full lift state, the flow rate of the main flow can be further increased. In addition, the amount of fuel which is hardly attracted to the main flow can be further reduced. Thus, the property for discharging the residual fuel can be further enhanced.
Further, according to the present embodiment, the total injection hole volume V2 is set to be larger than the seat downstream volume V3 in the valve closed state. For that reason, as compared with the case where the total injection hole volume V2 is set to be smaller than the seat downstream volume V3, the flow rate of the main flow can be further increased. In addition, the amount of fuel which is hardly attracted to the main flow can be further reduced. Thus, the property for discharging the residual fuel can be further enhanced.
Further, according to the present embodiment, the total injection hole volume V2 is set to be larger than the seat downstream volume V3 in the state in which the needle 20 is unseated from the seating surface 11s and is at the position farthest away in the movable range of the needle 20, that is, the needle 20 is at the full lift position. For that reason, as compared with the case in which the total injection hole volume V2 is set to be smaller than the seat downstream volume V3 in the full lift state, the flow rate of the main flow can be further increased. In addition, the amount of fuel which is hardly attracted to the main flow can be further reduced. Thus, the property for discharging the residual fuel can be further enhanced.
Further, according to the present embodiment, the total volume directly above the injection holes V4, which is the total volume of the volumes directly above the injection holes V4a, is set to be larger than the center volume V1 in the state in which the needle 20 is seated on the seating surface 11s, that is, in the valve closed state. For that reason, as compared with the case where the total volume directly above the injection holes V4 is set to be smaller than the center volume V1 in the valve closed state, the flow rate of the main flow can be further increased. Therefore, the amount of fuel which is hardly attracted to the main flow can be further reduced. Thus, the property for discharging the residual fuel can be enhanced.
Further, according to the present embodiment, the total of the peripheral lengths L5a of the multiple inflow ports 11in is defined as the total peripheral length L5. The virtual circle is in contact with the portions of the peripheral edges of the multiple inflow ports 11in which are closest to the axis line C1. The virtual circle is centered on the axis line C1. The peripheral length of the virtual circle is defined as the virtual peripheral length L6. The total peripheral length L5 is set to be larger than the virtual peripheral length L6. For that reason, as compared with the case in which the total peripheral length L5 is set to be smaller than the virtual peripheral length L6, the flow rate of the main flow can be further increased. Therefore, the amount of fuel which is hardly attracted to the main flow can be further reduced. Thus, the property for discharging the residual fuel can be enhanced.
Further, according to the present embodiment, the multiple injection holes 11a are placed at equal intervals on the concentric circle about the axis line C1 when viewed along the direction of the axis line C1. In other words, the inter-injection hole distances L are equal for all of the injection holes 11a. For that reason, the configuration enables to promote the uniform fuel flow into all the injection holes 11a. Therefore, the pressure loss caused when the fuel flows from the sac chamber Q22 into the inflow ports 11in can be reduced.
Further, according to the present embodiment, the inter-injection hole distance L is smaller than the diameter (short side length) of the inflow ports 11in. For that reason, the inflow angle θ2 of the lateral inflow fuel Y3b becomes smaller than that in a case in which the inter-injection hole distance L is larger than the diameter of the inflow ports 11in. Therefore, the configuration enables to promote the effect of reducing the increase in the pressure loss of the lateral inflow fuel Y3b.
According to the present embodiment, the surface roughness of the portion of the injection hole body 11 forming the fuel passage 11b is rougher than the surface roughness of the portion forming the inner wall surface of the injection hole 11a. For that reason, a pressure loss of the fuel flowing through the injection hole 11a can be reduced and the flow velocity can be increased as compared with the case where both of the fuel passage 11b and the injection hole 11a are set to have the same surface roughness. In the configuration, the fuel existing in the volume directly above the injection hole V4a flows thereby to enable to accelerate the main flow in the sac chamber Q22. Thus, the operation for attracting the fuel around the main flow toward the main flow can be enhanced. This configuration enables to enhance the property for discharging the residual fuel. Therefore, the fuel in the sac chamber Q22 can be discharged rapidly immediately after the valve has been closed. Thus, the property for discharging the foreign matter staying in the sac chamber Q22 can be promoted.
Further, the fuel injection system according to the present embodiment includes the control device 90 that controls the fuel injection state from the injection holes 11a by controlling the state in which the needle 20 is unseated from and seated on the seating surface 11s. The fuel injection system further includes the fuel injection valve 1. The control device 90 includes the multi-stage injection control unit 91 that controls the fuel injection valve 1 so as to inject the fuel from the injection hole 11a for multiple times in one combustion cycle of the internal combustion engine. In the configuration of the multi-stage injection, the number of leakage of fuel occurring in one combustion cycle increases. In addition, the injection pressure decreases in each injection. Therefore, the leaked fuel tends to adhere to the body outer surface 114, and deposits tend to accumulate. According to the present embodiment, the configuration, in which the inter-injection hole distance L is set to be smaller than the inflow port gap distance H, is employed in the fuel injection system that performs multi-stage injection. Therefore, the configuration enables to suitably exhibit the effect of reducing the amount of fuel leakage as described above.
Furthermore, according to the present embodiment, the control device 90 includes the PL injection control unit 92 that controls the fuel injection valve 1 to initiate the valve closing operation after the needle 20 has been unseated from the seating surface 11s and before reaching the maximum valve open position (full lift position). In such PL injection, the injection is likely to be performed at a low pressure. Therefore, the leaked fuel is likely to adhere to the body outer surface 114 of the body, and the deposit is likely to be developed. Therefore, according to the present embodiment, the configuration, in which the inter-injection hole distance L is set to be smaller than the inflow port gap distance H, is employed in the fuel injection system that performs the PL injection. Thus, the configuration enables to suitably exhibit the effect of reducing the amount of fuel leakage as described above.
Further, according to the present embodiment, the control device 90 includes the compression stroke injection control unit 93 that controls the fuel injection valve 1 so as to inject the fuel from the injection holes 11a in a period including a part of the compression stroke period of the internal combustion engine. In the compression stroke injection, the pressure outside the injection holes 11a, that is, the pressure of the combustion chamber 2 continues to rise even immediately after the valve has been closed. Therefore, the residual fuel is hardly discharged. Therefore, according to the present embodiment, the configuration, in which the inter-injection hole distance L is set to be smaller than the inflow port gap distance H, is employed to the fuel injection system for performing the compression stroke injection. Therefore, the configuration enables to suitably exhibit the effect to enhance the property for discharging the residual fuel discharging as described above.
In the above-described first embodiment, the entirety of the body bottom surface 112 is in the curved shape. To the contrary, in the present embodiment, as shown in
In the first embodiment, all of the multiple injection holes 11a are in the same shape. In this regard, in the present embodiment, as shown in
Operational effects of the placement will be described below with reference to
When the fuel flowing from the seat upstream passage Q10 into the first inter-injection hole portion 112a1 branches into the small injection hole 11a3 and the large injection hole 11a4, the fuel branches so as to flow more to the large injection hole 11a4 than to the small injection hole 11a3. For that reason, as shown in
On the other hand, the fuel flowing from the seat upstream passage Q10 into the second inter-injection hole portion 112a2 branches to each of the two large injection holes 11a4 so as to flow at a uniform flow rate when branching. For that reason, as shown in
Therefore, in an assumable case in which the large injection holes 11a4 and the small injection holes 11a3 are alternately placed contrary to the present embodiment, the second inter-injection hole portion 112a2 capable of decreasing the inflow angle θ as shown in
In the first embodiment, as shown in
Further, for example, in the configuration shown in
In the first embodiment, all of the multiple injection holes 11a are placed on the same inflow central virtual circle R2. On the other hand, in the present embodiment, as shown in
The operational effects of the placement described above are the same as those of the third embodiment, and the inflow angle θ2 is decreased to reduce the pressure loss. In other words, in an assumable case where the inner injection holes 11a5 and the outer injection holes 11a6 are alternately placed contrary to the present embodiment, the inter-injection hole portion 112a that can decrease the inflow angle θ2 does not exist. On the other hand, in the present embodiment, the multiple outer injection holes 11a6 are placed adjacent to each other. Therefore, there is the inter-injection hole portion 112a that can decrease the inflow angle θ2. Therefore, a pressure loss of the fuel flowing from the sac chamber Q22 into the injection hole 11a can be reduced.
In the present embodiment, similarly to the third embodiment, the inter-injection hole distances L, which are different from each other, exist. In the configuration, the smallest inter-injection hole distance L is set to be smaller than the inflow port gap distance H at the time of the full lift. Further, according to the present embodiment, the largest inter-injection hole distance L is also set to be smaller than the inflow port gap distance H at the time of the full lift. In a case where the inflow port gap distances H on both adjacent sides of the injection hole 11a are different from each other, the inflow port gap distance H which is larger is set to be larger than the inter-injection hole distance L. Further, according to the present embodiment, the inflow port gap distance H which is smaller is also set to be larger than the inter-injection hole distance L.
The injection holes 11a according to the first embodiment are each in a straight shape in which the passage cross-sectional area is uniform from the inflow port 11in to the outflow port 11out. The passage cross-sectional area is an area in a direction perpendicular to the axis line C2 of the injection hole 11a. The axis line C2 is the line connecting the center of the inflow port 11in and the center of the outflow port 11out. To the contrary, in the present embodiment, as shown in
As described above, in the present embodiment, the opening area of the inflow port 11in is larger than the opening area of the outflow port 11out. Therefore, the configuration enables to promote the inflow of the fuel from the sac chamber Q22 into the inflow port 11in immediately after the valve has been closed as compared with the case of the straight shape. Therefore, the discharging property of the residual fuel described above can be enhanced. In addition, the opening area of the inflow port 11in is larger than the opening area of the outflow port 11out, and therefore, the penetration force described above can be increased.
In the present embodiment, as shown in
As described above, also according to the present embodiment, the opening area of the inflow port 11in is larger than the opening area of the outflow port 11out in the same manner as in the fifth embodiment. Therefore, the configuration enables to enhance the property for discharging the residual fuel to increase the penetration force.
The fuel injection valve 1 according to the first embodiment includes the movable core 30 having the core facing surface 31c which is singular (refer to
On the other hand, a fuel injection valve 1A according to the present embodiment shown in
When the coil 17 is energized to open the needle 20, the movable core 30A is attracted toward the stationary cores 131 and 132 via both the first core facing surface 31c1 and the second core facing surface 31c2. As a result, the needle 20 performs the valve opening operation together with the movable core 30A, the coupling member 70, and the orifice member 71. When the needle 20 is at the full lift position , the coupling member 70 is in contact with a stopper 131a fixed to the first stationary core 131, and the first core facing surface 31c1 and the second core facing surface 31c2 do not make contact with the stationary cores 131 and 132, respectively.
When the energization of the coil 17 is stopped in order to close the needle 20, the resilient force of the second spring member SP2 applied to the movable core 30 is applied to the orifice member 71. As a result, the needle 20 performs the valve closing operation together with the movable core 30A, the coupling member 70, and the orifice member 71.
A slide member 72 is equipped to the movable core 30A and operates to open and close together with the movable core 30A. The slide member 72 slides in the direction along the axis line C1 with respect to a cover 132a fixed to the second stationary core 132. In short, the needle 20, which operates to open and close together with the movable core 30A, the slide member 72, the coupling member 70, and the orifice member 71, is supported by the slide member 72 in the radial direction.
The fuel flowing into the flow channel 13a formed inside the stationary core 13 flows in order through an internal passage 71a of the orifice member 71, an orifice 71b formed in the orifice member 71, and an orifice 73a formed in a moving member 73. Thus, the fuel flows into the flow channel 12b. The moving member 73 is a member that moves along the direction of the axis line C1 so as to open and close the orifice 71b. When the moving member 73 opens and closes the orifice 71b, the degree of throttle of the flow channel between the flow channel 13a and the flow channel 12b is changed.
Also in the fuel injection valve 1A according to the present embodiment, the shape of the fuel passage 11b formed between an outer peripheral surface of the needle 20 and an inner peripheral surface of the injection hole body 11 is the same as that of the fuel injection valve 1 according to the first embodiment, and the inter-injection hole distance L is smaller than the inflow port gap distance H. Therefore, the fuel injection valve 1A including the movable core 30A having the two attraction surfaces also enables to achieve both reduction in the fuel leakage amount by reducing the volume of the seat downstream passage Q20 and reduction in the pressure loss by reducing the inter-injection hole distance L.
The fuel injection valve 1 according to the first embodiment includes the singular actuator having the coil 17, the stationary core 13, and the movable core 30. In addition, the actuator applies the valve closing force to the needle 20. On the other hand, a fuel injection valve 1B of the present embodiment shown in
Specifically, the stationary cores 13 and 130 and the coils 17 and 170 are fixed in the main body 12 at different positions in the direction of the axis line C1. Further, the two movable cores 30 and 30B are placed side by side in the direction of the axis line C1 at positions to face the attraction surfaces of the respective stationary cores 13 and 130. The movable cores 30 and 30B are fixed to the needle 20 and are slidably provided in the main body 12 along the direction of the axis line C1.
When the needle 20 is caused to perform the valve opening operation, the two coils 17 and 170 are energized to attract the two movable cores 30 and 30B toward the stationary cores 13 and 130, respectively. As a result, the needle 20 fixed to the movable cores 30 and 30B opens against the resilient force of the first spring member SP1. When the needle 20 is caused to perform the valve closing operation, the energization of the two coils 17 and 170 is stopped, and the needle 20 is caused to perform the valve closing operation by application of the resilient force of the first spring member SP1 to the movable core 30.
Also in the fuel injection valve 1B according to the present embodiment, the shape of the fuel passage 11b provided between the outer peripheral surface of the needle 20 and the inner peripheral surface of the injection hole body 11 is the same as that of the fuel injection valve 1 according to the first embodiment. In addition, the inter-injection hole distance L is smaller than the inflow port gap distance H. Therefore, the fuel injection valve 1B including the two actuators also enables to achieve both of the reduction in the fuel leakage amount by reducing the volume of the seat downstream passage Q20 and the reduction in the pressure loss by reducing the inter-injection hole distance L.
Although the multiple embodiments of the present disclosure have been described above, not only the combinations of the configurations explicitly shown in the description of each embodiment, but also the configurations of multiple embodiments may be partially combined even if those are not explicitly shown unless a problem arises in the combination in particular. Unspecified combinations of the configurations described in the multiple embodiments and the modification examples are considered to be also disclosed in the following description.
In the first embodiment, the seat angle θ is set to an angle smaller than 90 degrees, however may be set to 90 degrees. In this case, the seat angle θ may be an angle deviated from 90 degrees to a large value or a small value as long as the seat angle θ falls within an allowable range of processing accuracy or assembly accuracy.
In the example shown in
In the first embodiment, the inflow port gap distance H is defined as the gap distance at the inflow port center point A. On the other hand, the inflow port gap distance H may be defined as a gap distance at a position in the peripheral edge of the inflow port 11in farthest from the axis line C1, or may be defined as a gap distance at a position in the peripheral edge of the inflow port 11in closest to the axis line C1. Further, the inflow port gap distance H may be defined as a gap distance at a position in the peripheral edge of the inflow port 11in intersecting with the inflow central virtual circle R2.
In the first embodiment, in the configuration where the inter-injection hole distance L and the inflow port gap distance H of each of the multiple injection holes 11a are the same, the inter-injection hole distance L is set to be smaller than the inflow port gap distance H. On the other hand, when different inter-injection hole distances and different inflow port gap distances arise, at least one inter-injection hole distance may be set to be smaller than at least one inflow port gap distance. Alternatively, the inter-injection hole distance between the two adjacent injection holes 11a may be set to be smaller than the inflow port gap distance of either one of those two injection holes 11a.
In the first embodiment, the inflow port gap distance H, which is the size of the gap between the outer surface of the needle 20 and the inflow port 11in, is the separation distance from the needle 20 at the center point A of the inflow port 11in. On the other hand, the inflow port separation distance may be the separation distance between the needle 20 and a portion of the injection hole 11a other than the center point A. For example, the inflow port gap distance H may be a separation distance in the direction of the axis line C1 at a position in the injection hole 11a farthest from the needle 20 or may be a separation distance in the direction of the axis line C1 at a position in the injection hole 11a nearest to the needle 20.
In each of the above embodiments, the fuel injection valves 1, 1A, and 1B are used to inject a gasoline fuel from the injection holes 11a, however a fuel injection valve to inject an ethanol fuel or a methanol fuel from the injection holes 11a may be used. An ethanol fuel and a methanol fuel have higher viscosity than that of a gasoline fuel. Therefore, the pressure loss of the ethanol fuel and the methanol fuel flowing through the fuel passage 11b and the injection hole 11a is large. In particular, a pressure loss occurring when the fuel is bent and flows from the sac chamber Q22 into the inflow ports 11in is large. For that reason, in an assumable case where the inflow port gap distance H is reduced to reduce the volume of the seat downstream passage Q20, the change in the flow velocity immediately after flowing in from the inflow port 11in becomes large. Therefore, there is a concern that cavitation occurs in the injection holes 11a. In view of the above concern, according to the present embodiment, the inter-injection hole distance L is set to be smaller than the inflow port gap distance H, as described above. Therefore, the increase in pressure loss can be mitigated by reducing the inter-injection hole distance L. Therefore, as compared with the case where the inter-injection hole distance L is set to be larger than the inflow port gap distance H, the concern of the occurrence of cavitation can be reduced.
According to the first embodiment, the fuel injection valve 1 is of a center placement type. The fuel injection valve 1 is attached to a portion of the cylinder head located at the center of the combustion chamber 2. Fuel is injected from above the combustion chamber 2 in the direction of the center line of the piston. On the other hand, the fuel injection valve 1 may be of a side placement type fuel injection valve which is attached to a portion of the cylinder block located on a lateral side of the combustion chamber 2 and injects the fuel from the lateral side of the combustion chamber 2.
According to the first embodiment, ten injection holes 11a are formed, however, the number of the injection holes is not limited to 10. The number of the injection holes may be other number as long as being 2 or more and may be, for example, 8.
According to the first embodiment, the movable portion M is supported in the radial direction at two positions including a portion (needle tip portion) of the needle 20, which faces the inner wall surface 11c of the injection hole body 11, and the outer peripheral surface 51d of the cup 50. In the seventh embodiment, the movable portion is supported in the radial direction at two positions including the needle tip portion and the slide member 72. On the other hand, the movable portion M may be supported in the radial direction at two positions including the outer peripheral surface of the movable core 30 and the needle tip portion.
According to the first embodiment, the inner core 32 is made of a nonmagnetic material, but may be formed of a magnetic material. In an assumable case where the inner core 32 is made of the magnetic material, the inner core 32 may be made of a weak magnetic material having a weaker magnetic property than that of the outer core 31. Similarly, the needle 20 and the guide member 60 may be made of a weak magnetic material that is weaker than that of the outer core 31.
According to the first embodiment, when the movable core 30 is moved by the predetermined amount, the cup 50 is interposed between the first spring member SP1 and the movable core 30 in order to materialize a core boost structure in which the movable core 30 makes contact with the needle 20 to start the valve opening operation. On the other hand, the cup 50 may be eliminated. In this configuration, a third spring member different from the first spring member SP1 may be provided, and a core boost structure may be employed in which the movable core 30 is urged toward the injection hole side by the third spring member.
As shown in
In the case of the structure shown in
In the structure formed with the recess portion d shown in
As shown in
As shown in
As described above, a region surrounded by the straight line L10 connecting the portions closest to the axis line C1 of the respective peripheral edges of the inflow ports 11in is referred to as a virtual region. As shown in
In each of the embodiments described above, the injection holes 11a are formed in the body bottom surface 112 among the tapered surface 111, the body bottom surface 112, and the coupling surface 113, which form the fuel passage 11b. On the other hand, the injection holes 11a may be formed in the portion of the tapered surface 111 on the downstream side of the seating surface 11s or may be formed in the coupling surface 113 of the tapered surface 111.
In each of the above embodiments, the needle 20 is configured to be movable relative to the movable core 30. It is noted that the movable core 30 and the needle 20 may be integrally configured so as not to be movable relative to each other. When the second and subsequent injections related to the divided injection are performed, it is necessary for the movable core 30 to return to its initial position. However, in a case where the movable core 30 and the needle 20 are integrally formed as described above, the needle 20 becomes heavy, and the valve closing bounce tends to occur. For that reason, the effect of reducing the bounce by setting the seat angle θ to 90 degrees or less is suitably exhibited in the case of the above-mentioned integrated configuration.
It should be appreciated that while the processes of the embodiments of the present disclosure have been described herein as including a specific sequence of steps, further alternative embodiments including various other sequences of these steps and/or additional steps not disclosed herein are intended to be within the steps of the present disclosure.
While the present disclosure has been described with reference to preferred embodiments thereof, it is to be understood that the disclosure is not limited to the preferred embodiments and constructions. The present disclosure is intended to cover various modification and equivalent arrangements. In addition, while the various combinations and configurations, which are preferred, other combinations and configurations, including more, less or only a single element, are also within the spirit and scope of the present disclosure.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2018-42226 | Mar 2018 | JP | national |
