JP5152043B2 - Fuel injection valve - Google Patents

Description

  The present invention relates to a fuel injection valve.

  Conventionally, a fuel injection valve using an actuator such as a piezo actuator having a large driving force has been proposed as an actuator for controlling a valve element that opens and closes an injection hole (see Patent Document 1). In this type of fuel injection valve, the valve element is driven by changing the pressure of the control pressure chamber by displacing the piston by an actuator.

  In the apparatus disclosed in Patent Document 1 as a kind of such fuel injection valve, a valve member that receives in the valve opening direction a fuel pressure that increases or decreases in the control pressure chamber due to advance or retreat of the piston is provided as the valve element.

  In this technique, a housing that supports at least the valve member so as to be movable in the axial direction is provided, and the housing supplies fuel to the control pressure chamber and the nozzle hole at both axial ends of the valve member, respectively. A supply chamber is formed. The valve member and the housing are provided with sliding portions so as to separate the control pressure chamber and the fuel supply chamber.

  In this sliding portion, the housing in the sliding portion has a sufficient thickness for ensuring strength in order to ensure separation between the control pressure chamber and the fuel supply chamber, in other words, fuel sealing performance.

JP 2006-214317 A

  In recent years, in order to improve engine combustion, an injection technique that performs split injection in which fuel injection is divided into a plurality of stages in one cycle of engine combustion is desired. Therefore, the fuel injection valve is required to have fuel injection controllability for accurately injecting a minute injection amount.

  However, in the prior art disclosed in Patent Document 1, although a sliding portion having a sufficient thickness for securing the strength is provided in order to ensure the fuel sealability between the control pressure chamber and the fuel supply chamber, the increase and decrease in the control pressure chamber. Since the fuel pressure to be used is the driving force of the valve member, the occurrence of pressure pulsation in the fuel supply chamber is inevitable at the start of driving of the valve member.

  If this pressure pulsation occurs excessively, there is a concern that the fuel injection controllability in a low injection amount region such as a minute injection amount may be lowered.

  The present invention has been made in view of the above-described problems, and an object thereof is to provide a fuel injection valve capable of improving fuel injection controllability in a low injection amount region.

  In order to achieve the above object, the present invention comprises the following technical means.

That is, in the inventions according to claims 1 to 7 , a valve member that opens and closes the nozzle hole, an actuator that expands and contracts in the axial direction, a piston that moves forward and backward in the axial direction according to the expansion and contraction of the actuator, and the nozzle hole are formed. And a housing for housing the valve member and the piston, wherein a fuel supply chamber for supplying fuel to the nozzle hole is formed on one end portion side of the valve member, and a piston that advances and retreats on the other end portion side of the valve member a housing defining a control pressure chamber which the pressure is increased or decreased, is fixed to the housing, with relative sliding along the valve member, and the cylindrical member you separate the control pressure chamber and the fuel supply chamber, A fuel reservoir chamber that is provided on the outer peripheral side of the cylindrical member and applies internal pressure to the cylindrical member; and the fuel reservoir chamber and the fuel supply chamber communicate with each other;
The cylindrical member is a flange portion that extends outside the cylindrical member, and has a flange portion that separates the fuel reservoir chamber and the control pressure chamber .

In this invention, the nozzle hole is formed, and the housing for accommodating the valve member and the piston forms a fuel supply chamber for supplying fuel to the nozzle hole on one end side of the valve member, and on the other end side of the valve member. A control pressure chamber is formed in which the internal pressure is increased or decreased by the piston moving forward and backward. The tubular member fixed to the housing is adapted to slide relatively along the valve member, it separates the control pressure chamber and the fuel supply chamber.

According to the first aspect of the present invention, it is possible to ensure separation of the control pressure chamber and the fuel supply chamber, that is, fuel sealability, by sliding the cylindrical member on the valve member.
Further, in the first aspect of the present invention, the cylindrical member has a flange portion that extends to the outside of the cylindrical member, and separates the fuel reservoir chamber and the control pressure chamber. Features.
According to this, since the space part corresponding to the flange part extended to the outer side of a cylindrical member is made into a fuel reservoir chamber, the volume expansion of a fuel reservoir chamber can be aimed at according to the extension length of a flange part.

  Further, the first sliding portion includes a fuel reservoir chamber that communicates with the fuel supply chamber on the outer peripheral side of the cylindrical member and in which the internal fuel pressure is applied to the cylindrical member. It is no longer necessary to increase the thickness of the cylindrical member in order to ensure fuel sealability with the fuel supply chamber, that is, to ensure strength.

  Since such a cylindrical member is thinned, the volume of the fuel reservoir chamber can be secured on the outer peripheral side of the cylindrical member in the housing without increasing the size of the housing.

  In addition, since the fuel supply chamber communicating with the nozzle hole communicates with the fuel reservoir chamber, the volume of the fuel supply chamber increases, so that the pressure pulsation of the fuel supply chamber at the start of driving of the valve member is accelerated. Can be reduced. Therefore, since the pressure pulsation at the start of driving the valve member can be suppressed, the fuel injection controllability in the low injection amount region is not deteriorated, and the low fuel injection controllability can be improved.

According to a second aspect of the present invention, the housing has an inner wall that forms a fuel reservoir chamber and a control pressure chamber, and the cylindrical member is fixed to the inner wall.

  According to this, since the cylindrical member on the inner peripheral side of the fuel reservoir chamber is fixed to the inner wall of the first sliding portion, the cylindrical member is driven by the fuel pressure that increases or decreases in the control pressure chamber. It is possible to reliably slide relative to the valve member.

  According to this, since the space portion corresponding to the flange portion extending outward from the cylindrical member is a fuel reservoir chamber, the volume of the fuel reservoir chamber is increased according to the extension length of the flange portion. Can be planned.

The invention according to claim 3 is characterized in that the flange portion is press-fitted into the housing.

  In such an invention, the flange portion of the cylindrical member on the inner peripheral side of the fuel reservoir chamber is fixed to the inner wall of the first sliding portion. When the cylindrical member is integrally provided on the inner wall via the flange portion, the fuel reservoir chamber may become a complicated space such as a bag hole portion. When the fuel reservoir chamber is, for example, a bag hole portion, it is necessary to form the fuel reservoir chamber by special removal processing such as electrolytic processing or electric discharge processing, which may increase the manufacturing cost.

On the other hand, according to the third aspect of the present invention, the flange portion, that is, the cylindrical member having the flange portion is formed as a separate member from the housing, and the cylindrical member and the housing are integrated by press-fitting. Therefore, it is not necessary to use the above special removal process for the formation of the fuel reservoir chamber, so that an increase in manufacturing cost can be suppressed.

In a fourth aspect of the invention, the housing includes a seat portion on which the valve member is seated and separated, and the seat portion and the cylindrical member are formed coaxially with respect to the valve member.

  In this invention, since the cylindrical member and the housing are fixed directly or indirectly, the valve member that is slidably supported by the cylindrical member is seated on and separated from the seat portion without axial misalignment. There is a need.

On the other hand, according to the invention described in claim 4 , since the seat portion and the cylindrical member are formed coaxially with respect to the valve member, the valve member is slidably supported by the cylindrical member. At the same time, the seat can be securely seated and separated from the seat without axis misalignment.

According to a fifth aspect of the present invention, the control pressure chamber is increased from the fuel pressure in the fuel supply chamber by changing the pressure by the piston that moves forward and backward.

  In this invention, the fuel pressure that increases or decreases in the control pressure chamber is increased from the fuel pressure in the fuel supply chamber, and therefore, pressure pulsation in the fuel supply chamber is likely to occur at the start of driving of the valve member. However, in the fuel injection valve according to any one of claims 1 to 5, the volume of the fuel supply chamber is increased by communicating with the fuel reservoir chamber. It is possible to effectively suppress the pressure pulsation.

In the invention according to claim 6 , the valve member is provided with a first shaft portion that receives the pressure of the control pressure chamber in the valve opening direction, and has a smaller diameter than the first shaft portion, and a second sliding portion is formed. A second shaft portion, and a fuel supply passage that is provided inside the first shaft portion and the second shaft portion and is supplied to the fuel supply chamber,
The housing has a support portion that slidably supports the first shaft portion, and the support portion is provided so as to separate the supply passage and the control pressure chamber.

  According to this, since the fuel supply chamber and the supply passage for supplying fuel to the nozzle hole are not arranged in the fuel reservoir chamber, the fuel reservoir chamber can be arranged on the entire circumference in the circumferential direction of the cylindrical member. It becomes. Therefore, since the volume of the fuel reservoir chamber can be easily increased, it is possible to prevent pressure pulsation at the start of driving of the valve member due to the increase in the volume of the fuel supply chamber.

The invention according to claim 7 is characterized in that the support portion is loosely fitted inside the housing.

  According to this, since the support portion is loosely fitted inside the housing, both the support portion and the cylindrical member that slidably support the valve member are off-axis by the support member loosely fitted inside the housing. Is acceptable. Thereby, since a support part and a cylindrical member can be formed, without raising the processing precision, the raise of manufacturing cost can be suppressed.

It is sectional drawing which shows the fuel injection valve by embodiment of this invention. FIGS. 2A and 2B are schematic views showing a characteristic portion of the fuel injection valve of FIG. 1. FIG. 2A is a cross-sectional view showing the characteristic portion, and FIG. It is explanatory drawing to do. It is a time chart explaining the action | operation of the fuel injection valve of FIG. FIG. 4A is a schematic diagram illustrating a fuel injection valve according to a comparative example, in which FIG. 4A is a cross-sectional view showing the fuel injection valve of the comparative example, and FIG. 4B acts on a sliding portion in FIG. It is explanatory drawing explaining the pressure state to do.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In addition, the overlapping description is abbreviate | omitted by attaching | subjecting the same code | symbol to the component corresponding in each embodiment.

  1 and 2 show a fuel injection valve according to an embodiment of the present invention. 1 shows a state in which the injection hole 57 is closed, and the fuel injection valve 1 in FIG. 2 (a) shows that the fuel injection valve 1 starts driving the valve member, that is, when the injection hole 57 starts to open. Is shown. The fuel injection valve 1 is attached so that fuel can be directly supplied to each cylinder of an internal combustion engine (not shown).

  The fuel injection valve 1 includes an actuator 2 and a valve element 3 including a piston 37 and a valve member 31. The actuator 2 and the valve element 3 are accommodated in a rod-shaped housing 5 side by side in the axial direction.

  The housing 5 includes a holder body 51 that houses a part of the actuator 2 and the valve element 3, and a nozzle body 55 that houses a part of the valve element 3. The holder body 51 and the nozzle body 55 accommodate the actuator 2 and the valve element 3 therein, and these constituent elements 51 and 55 are fastened and fixed by fastening means such as a retaining nut 61.

  The holder body 51 is formed in a cylindrical shape having a cavity inside. The upper end 52 of the holder body 51 (the end opposite to the nozzle body 55) supports the upper end of the actuator 2. A valve element 3 is disposed at the lower end of the actuator 2. The lower end is open and the nozzle body 55 is connected. A suction port 54 for supplying fuel into the holder body 51 is formed in the side wall 53 of the holder body 51.

  The nozzle body 55 is formed in a cylindrical shape having a hollow inside, and the lower end portion 56 (the side opposite to the holder body 51) is closed. The cavity of the nozzle body 55 is connected to the cavity of the holder body 51. The lower end portion 56 is formed with a nozzle hole 57 that communicates the inside of the nozzle body 55 and the outside of the nozzle body 55. The number of nozzle holes 57 is not limited to one as shown in FIG. 1, and a plurality of nozzle holes 57 may be provided.

  The fuel that has flowed into the holder body 51 flows into the nozzle body 55 through the actuator chamber 103 and the back pressure chamber 102, and is injected through the injection hole 57. The opening and closing of the nozzle hole 57 is controlled by the valve element 3.

  The actuator 2 includes a piezo stack 21, a fixing member 23, a displacement extraction portion 24, an elastic member 25, a casing 26, and the like. The piezo stack 21 is formed by stacking a plurality of plate-like piezo elements 22 in the plate thickness direction, and is housed in a cylindrical casing 26. As shown in FIG. 1, when a voltage is applied from the outside of the fuel injection valve 1, the piezo stack 21 extends in the thickness direction of the piezo element 22 in accordance with the magnitude of the applied voltage. When released, the piezo element 22 contracts and returns to the state before the voltage is applied.

  The fixing member 23 is fixed to one end of the casing 26. The fixing member 23 supports one end of the piezo stack 21 opposite to the valve element 3.

  The displacement extraction portion 24 is supported on the inner peripheral side of the casing 26 so as to be slidable in the axial direction. The displacement extraction part 24 is supported by the other end of the piezo stack 21. The end of the displacement extraction portion 24 on the valve element 3 side protrudes downward from the end of the casing 26. The lower end portion of the displacement extraction portion 24 is always in contact with a hydraulic pressure generation portion 36 that is a part of the valve element 3.

  The elastic member 25 is configured by an annular diaphragm or bellows, and even if the displacement extraction portion 24 reciprocates in the axial direction, the fuel filled outside the casing 26 enters the inside of the casing 26. Suppress.

  When a predetermined voltage is applied to the piezo stack 21 of the actuator 2, the piezo stack 21 extends a predetermined length according to the magnitude of the applied voltage. Since the movement of the upper portion of the piezo stack 21 is restricted by the fixing member 23, when the piezo stack 21 is extended, the other end of the piezo stack 21 with which the displacement extraction portion 24 is in contact is extended downward. Move by the amount corresponding to. Along with this, the displacement extraction unit 24 also moves downward by an amount corresponding to the extension amount of the piezo stack 21.

  Thereafter, when the application of the voltage is released, the piezo stack 21 contracts and returns to the state before the voltage is applied. Along with this, the displacement extraction unit 24 also moves to the original position.

  The valve element 3 disposed below the actuator 2 includes a valve member 31, a hydraulic pressure generator 36 including a piston 37, and the like.

  The valve member 31 controls the injection and non-injection of the fuel from the injection hole 57 by the front end 32 being separated from and seated on the seat portion 55 a on the inner wall of the lower end portion 56 of the nozzle body 55. The valve member 31 is formed in a substantially cylindrical shape. The valve member 31 includes a first shaft portion 31a, a second shaft portion 31b, and a third shaft portion 31c whose outer diameter decreases toward the distal end 32. The lower end side of the first shaft portion 31a, the second shaft Two stepped portions 33 and 34 are formed on the lower end side of the portion 31b.

  In the valve member 31, the side wall between the stepped portion 33 and the stepped portion 34, that is, the second shaft portion 31 b is supported by the inner wall of the nozzle body 55 so as to be slidable in the axial direction. The structure of the sliding portion where the valve member 31 and the nozzle body 55 slide will be described later.

  Inside the valve member 31, a fuel supply passage 35 is formed as a “supply passage” extending in the axial direction from the upper end portion to the vicinity of the lower step portion 34. Specifically, the fuel supply passage 35 communicates with the upper end portion and the step portion 34, and opens to the side wall of the step portion 34.

  The nozzle body 55 forms an accommodating chamber 202 as a “control pressure chamber” that surrounds the step portion 33 between the first shaft portion 31 a of the valve member 31. The accommodation chamber 202 accommodates an internal cylinder 47 and a spring 48 as “supporting portions”. The interior cylinder 47 supports the side wall of the first shaft portion 31a so as to be slidable in the axial direction. The upper end portion of the interior cylinder 47 abuts on the outer wall of the lower end portion of a cylinder 39 described later. The spring 48 is disposed between the bottom of the storage chamber 58 and the lower end of the interior cylinder 47, and always urges the interior cylinder 47 upward.

When the internal cylinder 47 comes into contact with the outer wall at the lower end of the cylinder 39, the back pressure chamber 102 and the storage chamber 58 communicating with the fuel supply passage 35 are partitioned.

The fuel that has flowed in from the upper side of the fuel supply passage 35, that is, from the actuator chamber 103 and the back pressure chamber 102, is discharged to the fuel supply chamber 101 through the fuel supply passage 35. In a state where the nozzle hole 57 is closed by the valve member 31, the fuel that has flowed into the fuel supply chamber 101 remains there. When the injection hole 57 is opened by the valve member 31, the fuel in the fuel supply chamber 101 is injected outside through the injection hole 57. A spring 49 that biases the valve member 31 in the valve closing direction is accommodated in the back pressure chamber 102 above the fuel supply passage 35.

  The fuel that has flowed into the holder body 51 flows into the fuel supply passage 35. The hydraulic pressure generated by the hydraulic pressure generator 36 described later flows into the storage chamber 202. Then, the hydraulic pressure generated by the hydraulic pressure generator 36 acts on the step portion 33.

  The hydraulic pressure generating unit 36 is disposed between the valve member 31 and the actuator 2, and drives the valve member 31 by converting the displacement amount of the displacement extracting unit 24 into an oil pressure at the start of driving of the valve member 31. It is a hydraulic mechanism that generates a driving force. The hydraulic pressure generating unit 36 includes a piston 37, a cylinder 39, a slit spring 44, and the like.

  The piston 37 is formed in a columnar shape, and the outer wall of the upper end portion is disposed in contact with the displacement extraction portion 24. The lower end side of the piston 37 is accommodated in a cylinder 39 formed in a cylindrical shape having a bottom 41 so as to be slidable in the axial direction. The cylinder 39 forms a hydraulic pressure chamber 201 between the lower end portion of the piston 37, that is, the top portion. The cylinder 39 is supported on the upper end portion of the nozzle body 55 and is accommodated in the holder body 51.

  The hydraulic chamber 201 is always filled with fuel, and the volume of the hydraulic chamber 201 is reduced by moving the piston 37 downward. Therefore, the downward movement of the piston 37 increases the pressure of the hydraulic chamber 201. Acts as follows. The upward movement of the piston 37 acts to lower the pressure in the hydraulic chamber 201. The hydraulic pressure chamber 201 has a sliding gap between the piston 37 and the cylinder 39 due to a hydraulic pressure difference generated between the hydraulic pressure chamber 201 and the periphery of the hydraulic pressure generating portion 36 when the piston 37 moves upward. Via which the fuel is filled.

  The lower end portion of the cylinder 39 communicates the first series passage 42 communicating with the hydraulic pressure chamber 201 and the storage chamber 202, and the back pressure chamber 102 communicating with the fuel supply passage 35 of the valve member 31 and the actuator chamber 103. A second communication path 43 is formed. In FIG. 1, the first series passage 42 and the second communication path 43 appear to be connected, but the first series path 42 and the second communication path 43 are not connected.

  A slit spring 44 is disposed around the cylinder 39. The slit spring 44 has a known configuration and exhibits spring characteristics by, for example, forming a plurality of slits extending in the circumferential direction on a cylindrical member. The upper end portion of the slit spring 44 is supported by the piston 37 and the lower end portion is supported by the cylinder 39. The slit spring 44 urges the cylinder 39 and the piston 37 in a direction that always separates them while being accommodated in the fuel injection valve 1. The slit spring 44 applies a preload to the piezo stack 21 via the piston 37 and the displacement extraction portion 24. The preliminary load is set to such an extent that it does not hinder the piezo stack 21 from extending.

  When the piston 37 starts moving downward, the fuel pressure in the hydraulic pressure chamber 201 increases. The pressure is transmitted to the storage chamber 202 through the first series passage 42 and acts on the stepped portion 33 on the upper side of the valve member 31. In other words, when the downward movement of the piston 37 is started, the fuel pressure rising in the hydraulic pressure chamber 201 and the storage chamber 202 acts on the step portion 33 of the valve member 31, so that the valve member 31 has a valve opening direction. Liquid pressure acts.

  Next, the mechanism of the opening / closing operation of the valve member 31 will be described.

  The opening and closing operation of the valve member 31 includes the force generated by receiving the pressure of the fuel supplied into the fuel injection valve 1 from the suction port 54 and the pressure of the fuel generated in the hydraulic pressure chamber 201 of the hydraulic pressure generating unit 36. , Determined by the balance of the biasing force of the spring 49.

  In the valve member 31, an upward force (hereinafter referred to as “upward force”) is generated by the fuel pressure acting on the stepped portions 33 and 34 and the tip 32. The upward force is related to the pressure receiving areas of the step portions 33 and 34 and the tip 32 where the pressure of each fuel acts, and the pressure of each fuel, the fuel pressure in the storage chamber 202 and the fuel pressure in the fuel supply chamber 101. It depends on.

  The valve member 31 is subjected to the pressure of the fuel in the fuel supply passage 35, that is, the back pressure chamber 102, and a downward force (hereinafter referred to as “downward force”) due to the biasing force of the spring 49. Occur. The downward force is determined by the pressure receiving area of the valve member 31 to which the pressure of the fuel in the back pressure chamber 102 acts, the pressure of the fuel in the passage 35, and the biasing force of the spring 49.

  When the upper force wins over the lower force, the valve member 31 starts moving in the valve opening direction, and when the lower force wins over the upper force, the valve member 31 starts moving in the valve closing direction. To do.

  Here, when the valve member 31 starts to move in the valve opening direction, the tip 32 of the valve member 31 is separated from the seat portion 55 a of the nozzle body 55, so that an upward force acts on the tip 32. On the other hand, the top of the piston 37 and the stepped portion 33 of the valve member 31 are connected by the fuel in the hydraulic chamber 201 and the storage chamber 202, and the piston 37 and the valve member 3 are connected hydraulically. Therefore, the valve member 31 moves in a direction in which the differential pressure between the fuel pressure in the storage chamber 202 and the fuel pressure in the back pressure chamber 102 decreases.

  In other words, before the opening of the valve member 31, the fuel pressure in the hydraulic chamber 201 and the storage chamber 202 is temporarily higher than the fuel pressure in the fuel supply chamber 101, but after the opening of the valve member 31 is started. Is reduced in the direction in which the differential pressure from the fuel pressure in the fuel supply chamber 101 decreases.

  Specifically, in the valve opening operation of the valve member 31, the fuel pressure in the fuel supply chamber 101 and the back pressure chamber 102 is substantially the same as the pressure of the fuel flowing in from the suction port 54 before the valve opening is started. Therefore, it shows a substantially constant value corresponding to the pressure of the fuel supplied to the suction port 54. The pressure of the fuel in the hydraulic chamber 201 and the storage chamber 202 is intentionally increased by the hydraulic pressure generator 36 that is operated by the actuator 2, and the above-described differential pressure generated by this increase causes the “upward” to the tip 32. It is necessary to make up for the lack of power.

  In addition, in the valve closing operation of the valve member 31, the “upward force” shortage to the tip 32 does not occur, so the required differential pressure before starting the valve closing is the differential pressure before starting the valve opening. It may be small enough. That is, in the valve closing operation of the valve member 31, when the pressure of the fuel in the hydraulic chamber 201 and the storage chamber 202 is slightly reduced and the upper force exceeds the lower force, the valve member 31 moves in the valve closing direction. Move to.

  Next, the characteristic part of this embodiment is demonstrated based on FIG. FIG. 2A shows a sectional view showing the characteristic portion, and FIG. 2B shows a pressure state acting on the sliding portion related to the characteristic portion.

  The structure of the sliding part of the valve member 31 and the nozzle body 55 is as follows.

  That is, as shown in FIG. 2, the structure of the sliding portion includes a cylindrical member 58 that is a sliding portion on the nozzle body 55 side and a second shaft portion 31b that is a sliding portion on the valve member 31 side. Has been.

  The cylindrical member 58 is fixed to the inner wall of the nozzle body 55, and supports the second shaft portion 31b so as to be relatively slidable along the outer periphery of the second shaft portion 31b of the valve member 31.

  The space between the storage chamber 202 and the fuel supply chamber 101 is hydraulically sealed by a sliding gap between the inner periphery of the cylindrical member 58 and the second shaft portion 31b. The sliding gap is set to such an extent that fluctuations in the fuel pressure in the storage chamber 202 do not hinder the maintenance of a constant fuel pressure in the fuel supply chamber 101.

  The tubular member 58 includes a tubular portion main body 58a and a flange portion 58b extending outward in the radial direction of the tubular portion main body 58a. The flange portion 58 b is formed in a disc shape and is bridged to the step portion 55 b on the inner wall of the nozzle body 55. Specifically, the outer peripheral portion of the flange portion 58b is press-fitted into the inner wall of the nozzle body 55, and the outer peripheral portion is locked to the step portion 55b so that the movement is restricted by the step portion 55b of the inner wall.

  A fuel reservoir chamber 59 capable of storing fuel is provided on the outer peripheral side of the cylindrical portion main body 58a. The fuel reservoir chamber 59 is formed by the outer periphery of the cylindrical portion main body 58a and the flange portion 58b and the inner periphery of the inner wall of the nozzle body 55 on the stepped portion 55b side.

  Thereby, the fuel reservoir 59 can apply the pressure of the fuel in the fuel reservoir 59 to the outer periphery of the cylindrical member 58.

  The fuel reservoir chamber 59 is formed, for example, in the shape of a bag hole, and the lower side of the fuel reservoir chamber 59 communicates with the fuel supply chamber 101. Thereby, the volume of the fuel supply chamber 101 can be increased by the volume amount of the fuel reservoir chamber 59.

  Here, in the valve member 31, the second shaft portion 31b and the tip 32 are respectively supported by the inner periphery of the cylindrical portion main body 58a and the seat portion 55a when the tip 32 is seated. The cylindrical portion main body 58 a and the seat portion 55 a are formed so as to be coaxial with the valve member 31. Accordingly, the valve member 31 is slidably supported by the cylindrical member 58 and can be reliably seated and separated from the seat portion 55a without being misaligned.

  For example, as an example of the manufacturing method, the cylindrical member 58 is press-fitted into the inner wall of the nozzle body 55. The cylindrical member 58 and the nozzle body 55 are integrally fixed by press-fitting. Thereafter, the inner periphery of the cylindrical portion main body 58a and the surface of the sheet portion 55a on the lower end portion 56 side are coaxially processed.

  Next, the effect which the said characteristic part show | plays is demonstrated based on FIGS. FIG. 3 is a time chart for explaining the operation of the fuel injection valve 1. The characteristic indicated by the solid line in the figure indicates an example of fuel injection in the low injection amount region according to the invention of the present embodiment, and the characteristic indicated by the two-dot chain line indicates an injection region other than the low injection amount region, for example, a high injection amount. An example of fuel injection in a region is shown. Moreover, the characteristic shown with the broken line in a figure shows operation | movement with the fuel injection valve (refer FIG. 4) of a comparative example. FIG. 4 shows a structure of a comparative example (see FIG. 4A) and a pressure state acting on the sliding portion (see FIG. 4B).

  FIG. 3A shows a state of a drive signal (pulse) transmitted from the control device (not shown) to the actuator 2. In the drawing, a predetermined voltage is applied to the actuator 2 when it is in the ON state, and the application of the predetermined voltage to the actuator 2 is completed when it is in the OFF state. FIG. 3B shows the displacement of the piston 37. In the figure, the zero state indicates a state where the piston 37 is positioned above. FIG. 3C shows the state of the pressure of the fuel in the hydraulic chamber 201 and the storage chamber 202 as the “control pressure chamber”. FIG. 3D shows the state of the fuel pressure in the fuel supply chamber 101. FIG. 3 (e) shows the lift amount of the valve member 31, and in the figure, the state where the lift is zero indicates that the valve is closed. FIG. 3 (f) shows the injection rate of the fuel injected from the injection hole 57.

  Until the time t1, that is, until the drive signal is switched from OFF to ON, the position of the piston 37 is upward (see FIG. 3B). For this reason, the fuel pressure in the fluid pressure chamber 201 and the storage chamber 202 is substantially the same pressure P1 as the fuel pressure in the fuel supply chamber 101 and the back pressure chamber 102 (see FIG. 3C). In this state, since the upward force generated in the valve member 31 is lower than the downward force, the tip 32 of the valve member 31 maintains the state of being seated on the seat portion 55 a of the nozzle body 55, and the fuel from the injection hole 57. Is not jetted.

  When the driving signal is turned ON at time t1, the piston 37 is moved downward by the displacement extraction portion 24. The piston 37 is pushed downward, and the fuel pressure in the hydraulic chamber 201 and the storage chamber 202 starts to rise.

  When the pressure of the fuel in the hydraulic chamber 201 and the storage chamber 202 rises to some extent and at time t2, the increased pressure P2 acts on the upper step portion 33, so the upper force generated in the valve member 31 is the lower force. Better than. Thereby, the valve member 31 begins to lift in the valve opening direction. When the valve member 31 is lifted in the valve opening direction, the fuel in the fuel supply chamber 101 is injected from the injection hole 57 (see FIG. 3F).

  From time t2 to time t3, since the piston 37 and the valve member 31 are hydraulically connected, when the valve member 31 starts to lift, the fuel pressure in the hydraulic chamber 201 and the storage chamber 202 and the fuel supply chamber 101 are increased. In addition, since the differential pressure from the fuel pressure in the back pressure chamber 102 acts in the reduction direction, the pressure in the hydraulic chamber 201 and the storage chamber 202 decreases.

  When the drive signal is switched from ON to OFF at time t3, the piston 37 is moved upward by the slit spring 44, so that the fuel pressure in the hydraulic chamber 201 is temporarily reduced. From time t3 to time t4, as the piston 37 moves upward, the pressure in the hydraulic pressure chamber 201 and the storage chamber 202 becomes lower than the fuel pressure in the fuel supply chamber 101 and the back pressure chamber 102. At this time, the lift of the valve member 31 maintains the valve open state.

  When the pressure of the fuel in the hydraulic chamber 201 and the storage chamber 202 drops to some extent and at time t4, the lowered pressure P3 acts on the upper step portion 33, so that the downward force generated in the valve member 31 is Overpower. Thereby, the valve member 31 begins to move in the valve closing direction. Thereafter, the tip 32 of the valve member 31 is seated on the seat portion 55a of the nozzle body 55, and fuel injection from the injection hole 57 is stopped (see FIG. 3 (f)).

  In the present embodiment in which the fuel injection valve 1 operates as described above, the pressure pulsation in the fuel supply chamber 101 that occurs when the valve member 31 starts to be driven, that is, when the valve member 31 starts to open can be reduced early. It becomes.

  First, the fuel injection valve of the comparative example shown in FIG. 4 will be described. When describing the fuel injection valve of the comparative example, members common to the fuel injection valve of the present embodiment will be described using the same member names and numbers as those of the fuel injection valve of the present embodiment. As shown in FIG. 4 (a), the fuel injection valve of the comparative example has no fuel reservoir chamber 59 on the inner wall of the sliding portion on the nozzle body 55 side, so that the inner wall has a sufficient thickness. Is secured.

  That is, as shown in FIG. 4B, an internal pressure due to the liquid pressure of the fuel is applied to the inner wall on the nozzle body 55 side by the fuel present in the sliding gap with the second shaft portion 31b. The pressure P2 of the fuel in the storage chamber 202 is applied to the end of the inner wall on the side of the storage chamber 202, and the fuel pressure P1 of the fuel supply chamber 101 is applied to the end of the inner wall on the side of the fuel supply chamber 101. Then, a pressure is formed by reducing the difference between the fuel pressure P2 in the storage chamber 202 and the fuel pressure P1 in the fuel supply chamber 101 toward the inside of the inner wall, and this pressure acts on the inner wall as the inner pressure. In such a fuel injection valve of the comparative example, the inner wall of the sliding portion on the nozzle body 55 side needs to be thick enough to ensure fuel sealability and stably maintain the sliding gap.

  On the other hand, in the fuel injection valve 1 of the present embodiment, although the internal pressure is applied to the inner periphery of the cylindrical portion main body 58a, the fuel pressure in the fuel reservoir chamber 59, that is, the fuel supply is also applied to the outer periphery of the cylindrical portion main body 58a. The fuel pressure P1 in the chamber 101 acts. Thereby, in order to stably maintain the sliding gap, the thickness of the cylindrical portion main body 58a may be set to a thickness that ensures strength against the pressure obtained by subtracting the pressure P1 from the internal pressure. In other words, in the present embodiment, the pressure of the fuel in the fuel reservoir chamber 59 is applied to the outer periphery of the cylindrical portion main body 58a, so that the thickness of the cylindrical portion main body 58a can be reduced. Thereby, the volume of the fuel reservoir chamber 59 can be secured in the inner wall of the nozzle body 55 without increasing the size of the fuel injection valve 1.

  Further, in the present embodiment, since the fuel reservoir chamber 59 is always in communication with the fuel supply chamber 101, the volume of the fuel supply chamber 101 increases. Therefore, when the valve member 31 starts to open, the fuel supply chamber 101 Can be reduced at an early stage (see FIG. 3D).

  As a result, the pressure pulsation due to the oil hammer of the fuel supply chamber 101 at the start of opening of the valve member 31 can be reduced early, so that the fuel injection rate can be stabilized as shown in FIG. The fuel injection controllability can be improved.

  That is, in the present embodiment, it is possible to ensure fuel injection controllability in which the relationship between the ON period of the drive signal and the fuel injection amount is linear even in the low injection amount region.

  In the present embodiment described above, the cylindrical member 58 having the cylindrical portion main body 58a and the flange portion 58b is fixed to the inner wall of the nozzle body 55 by the flange portion 58b, so that the storage chamber 202, the fuel reservoir chamber 59, The fuel supply chamber 101 can be partitioned.

  Moreover, since the flange portion 58b extends radially outward from the cylindrical portion main body 58a, the volume of the fuel reservoir 59 can be secured according to the extending length of the flange portion 58b. Thereby, the volume expansion of the fuel reservoir 59 becomes easy.

  Here, for example, when the cylindrical member 58 is integrally provided on the inner wall via the flange portion 58b, the fuel reservoir 59 may be a complicated space such as a bag hole portion. In such a case, the fuel reservoir chamber 59 needs to be formed by special removal processing such as electrolytic processing or electric discharge processing, which may increase the manufacturing cost.

  On the other hand, in this embodiment, the cylindrical member 58 is formed as a separate member from the nozzle body 55, and the cylindrical member 58 and the nozzle body 55 are integrated by press-fitting, so that the fuel reservoir chamber 59 is formed. Since it is not necessary to use the special removal process, an increase in manufacturing cost can be suppressed.

  In the present embodiment, the second shaft portion 31b and the tip 32 of the valve member 31 are formed coaxially with the inner periphery of the tubular portion main body 58a and the seat portion 55a when the tip 32 is seated. Accordingly, the valve member 31 is slidably supported by the cylindrical member 58 and can be reliably seated and separated from the seat portion 55a without being misaligned.

  Further, in the present embodiment, the hydraulic pressure chamber 201 and the storage chamber 202 are changed from the fuel pressure in the fuel supply chamber 101 and the back pressure chamber 102 by changing the pressure by the output extraction portion 24 that advances and retreats, that is, the piston 37. The pressure is increased. In such a configuration, since the driving force for driving the valve member 31 is likely to increase, pressure pulsation in the fuel supply chamber 101 is likely to occur when the valve member 31 starts to open. However, in the fuel injection valve 1 having the above-described characteristic portion, the fuel supply chamber 101 can be increased in volume by communicating with the fuel reservoir chamber 59, so that the pressure pulsation when the valve member 31 starts to open is effectively reduced. It can be suppressed.

  In the present embodiment, the back pressure chamber 102 on the upper side of the valve member 31 and the fuel supply chamber 101 on the lower side are communicated with each other through a fuel supply passage 35 formed inside the valve member 31. According to this, since the fuel supply chamber 101 and the fuel supply passage 35 are not disposed in the fuel reservoir chamber 59, the fuel reservoir chamber 59 can be disposed on the entire circumference in the circumferential direction of the cylindrical member 58. Become. Therefore, since the volume of the fuel reservoir chamber 59 can be easily increased, the pressure pulsation at the start of the valve opening of the valve member 31 due to the increase in the volume of the fuel supply chamber 101 can be prevented.

  In the present embodiment described above, the internal cylinder 47 that slides relative to the first shaft portion 31 a of the valve member 31 is loosely fitted into the nozzle body 55.

  According to this, both the internal cylinder 47 and the cylindrical member 58 that slidably support the valve member 31 are allowed to be misaligned by the support member loosely fitted inside the nozzle body 55. Thereby, since the interior cylinder 47 and the cylindrical member 58 can be formed without increasing the processing accuracy, an increase in manufacturing cost can be suppressed.

(Other embodiments)
Although a plurality of embodiments of the present invention have been described above, the present invention is not construed as being limited to these embodiments, and can be applied to various embodiments without departing from the scope of the present invention. .

  (1) In the present embodiment described above, the hydraulic pressure chamber 201 and the storage chamber 202 are configured to be increased from the fuel pressure in the fuel supply chamber 101 by changing the pressure by the piston 37 moving forward and backward. However, the present invention is not limited thereto, and a fuel injection valve that injects fuel may be used by configuring the hydraulic pressure chamber and the storage chamber to be depressurized from the fuel pressure in the fuel supply chamber.

  (2) In the present embodiment described above, the tubular member 58 is formed as a separate member from the nozzle body 55, and the tubular member 58 and the nozzle body 55 are integrated by press-fitting. Not limited to this, the cylindrical member 58 and the nozzle body 55 may be integrally formed.

DESCRIPTION OF SYMBOLS 1 Fuel injection valve 2 Actuator 3 Valve element 5 Housing 21 Piezo stack 22 Piezo element 23 Fixing member 24 Displacement extraction part 26 Casing 31 Valve member (valve element)
33 Stepped portion 34 Stepped portion 35 Fuel supply passage (supply passage)
36 Fluid pressure generator (valve element)
37 Piston 39 Cylinder 44 Slit spring 47 Internal cylinder (support)
48 Spring 49 Spring 51 Holder body (housing)
55 Nozzle body (housing)
55a Sheet portion 55b Stepped portion 57 Injection hole 58 Tubular member 58a Tubular portion main body 58b Flange portion 59 Fuel reservoir chamber 101 Fuel supply chamber 102 Back pressure chamber 103 Actuator chamber 201 Hydraulic chamber 202 Accommodating chamber (control pressure chamber)

Claims (7)

A valve member for opening and closing the nozzle hole;
An actuator that expands and contracts in the axial direction;
A piston that moves forward and backward in the axial direction according to the expansion and contraction of the actuator;
A housing for housing the valve member and the piston, wherein a fuel supply chamber for supplying fuel to the nozzle hole is formed on one end side of the valve member; On the other end side of the member, a housing that forms a control pressure chamber in which the internal pressure is increased or decreased by the piston moving forward and backward ,
Is fixed to the housing, with relative sliding along the valve member, and the cylindrical member you separating the fuel supply chamber and said control pressure chamber,
A fuel reservoir chamber provided on the outer peripheral side of the cylindrical member, and applying an internal pressure to the cylindrical member;
The fuel reservoir chamber and the fuel supply chamber communicate with each other,
The fuel injection valve according to claim 1, wherein the tubular member has a flange portion that extends to the outside of the tubular member and separates the fuel reservoir chamber and the control pressure chamber . The housing has an inner wall that forms the fuel reservoir chamber and the control pressure chamber;
The fuel injection valve according to claim 1, wherein the cylindrical member is fixed to the inner wall . The fuel injection valve according to claim 1 or 2, wherein the flange portion is characterized by being press-fitted into the housing. The housing includes a seat portion on which the valve member is seated and separated,
The fuel injection valve according to any one of claims 1 to 3 , wherein the seat portion and the cylindrical member are formed coaxially with respect to the valve member. The control pressure chamber, the pressure change by the piston to advance and retreat, the fuel injection according to claims 1, characterized in that it is boosted from the fuel pressure in the fuel supply chamber to one of claims 4 valve. The valve member is
A first shaft portion that receives the pressure of the control pressure chamber in a valve opening direction, a second shaft portion that is provided with a smaller diameter than the first shaft portion, and the second sliding portion is formed;
A fuel supply passage provided in the first shaft portion and the second shaft portion and supplied to the fuel supply chamber;
The housing is
A support portion for slidably supporting the first shaft portion;
The fuel injection valve according to claim 5 , wherein the support portion is provided so as to separate the supply passage and the control pressure chamber. The fuel injection valve according to claim 6 , wherein the support portion is loosely fitted inside the housing.

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