JP2002130088A - Solenoid type fuel injection valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a technique for reducing the manufacturing cost of a solenoid type fuel injection valve while keeping the adjustment precision of dynamic flow rate thereof. SOLUTION: This solenoid type fuel injection valve 1A comprises a substantially cylindrical body 41; a valve 9 reciprocating in the body 41; a spring 36 located on the upstream side from the valve 9; a spring pin 32 abutting on the upstream end part of the spring 36; and a strainer 26 located on the upstream side from the spring pin 32. This valve 1A is characterized by that the strainer 26 is housed and integrated into the spring pin 32.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

[0001] The present invention relates to an electromagnetic fuel injection valve.

[0002]

2. Description of the Related Art An example of a conventional electromagnetic fuel injection valve will be described with reference to FIG. FIG. 5 is a longitudinal sectional view of an electromagnetic fuel injection valve according to the related art. The electromagnetic fuel injection valve 100 shown in FIG. 5 includes a substantially cylindrical body 141, a valve 109 that reciprocates in the body 141, a spring 136 located upstream of the valve 109,
The spring 136 includes a spring pin 132 that contacts an upstream end of the spring 136, and a strainer 126 (including the metal collar 102) positioned upstream of the spring pin 132. In this electromagnetic fuel injection valve, the spring pin 132 and the strainer 126 are formed separately, and each is press-fitted and fixed to the body 141.

Another example of an electromagnetic fuel injection valve according to the prior art will be described with reference to FIGS. 6 and 7. FIG. FIG. 6 is a longitudinal sectional view of a conventional electromagnetic fuel injection valve, and FIG. 7 is a perspective view of the strainer. The electromagnetic fuel injection valve 200 shown in FIG. 6 includes a substantially cylindrical body 241, a valve 209 reciprocating in the body 241, a spring 236 located upstream of the valve 209, and an upstream of the spring 236. A spring pin (inner collar) 232 abutting on the side end;
And a strainer 226 located on the upstream side of P. 32. As shown in FIG. 7, the strainer 226 has a cylindrical portion 226A, a channel portion 226B formed inside the cylindrical portion 226A, and a channel 226B extending from a side wall of the cylindrical portion 226A. Passage 226D drilled
And a filter member 204 provided in the fuel passage 226D.
have. Reference numeral 226F indicates the upper end of the strainer 226. Reference number 226C is strainer 2
The lower end portion 226C is provided with an opening 226E at the lower end portion 226C. In this electromagnetic fuel injection valve, the upper end of the spring pin 232 is inserted into the opening 226E of the lower end 226C of the strainer 226, so that the strainer 226 and the spring pin 232 are inserted.
Are integrally attached. The integrated strainer 226 and spring pin 232 are
41 is press-fitted and fixed.

[0004]

When the spring pin 132 and the strainer 126 are formed separately as in the electromagnetic fuel injection valve 100 shown in FIG. 5, a step of press-fitting the spring pin 132 into the body 141, 13
2 are required. For this reason, there was a problem that manufacturing cost was high. Further, when the spring pin 132 is to be attached to the body 141 alone, the metal collar 102 for press-fitting and fixing the strainer 126 is required. For this reason, there has been a problem that the parts cost is high.

On the other hand, an electromagnetic fuel injection valve 200 shown in FIG.
In this case, there has been a problem that it is difficult to finely adjust the dynamic flow rate when the spring pin 232 is press-fitted and fixed in the body 241. That is, normally, in the electromagnetic fuel injection valve, the dynamic flow rate is adjusted by pressing the spring 236 with the spring pin 232 and adjusting the elastic force. For this purpose, it is necessary to adjust the elastic force of the spring 236 while gradually pressing the spring pin 232 into the downstream side. Here, the electromagnetic fuel injection valve 20 shown in FIG.
0, the upper end of the spring pin 232 is
6 is attached and integrated, the strainer 22
6 is pressed with a jig or the like. However, since the rigidity of the portion where the fuel passage 226D of the strainer 226 is opened is low, the strainer 2
When the upper end 226F of the fuel passage 22 is pressed, the cylindrical portion 226A near the fuel passage 226D is deformed.
6D itself also deforms. For this reason, the fuel passage 226D at the time of press-fitting (when pressing) and after the press-fitting is completed (when the pressing force is removed).
Since the flow path resistance changes due to different shapes and the like, it has been difficult to finely adjust the dynamic flow rate.

An object of the present invention is to provide a technique for reducing the manufacturing cost while maintaining the accuracy of adjusting the dynamic flow rate of the electromagnetic fuel injection valve.

[0007]

Means for Solving the Problems, Functions and Effects In order to solve the above problems, an electromagnetic fuel injection valve according to claim 1 comprises a substantially cylindrical body, a valve reciprocating in the body, The spring includes a spring located upstream of the valve, a spring pin abutting on the upstream end of the spring, and a strainer located upstream of the spring pin. The electromagnetic fuel injection valve is characterized in that the strainer is housed inside the spring pin and integrated. Here, "accommodating the strainer inside the spring pin"
This does not mean that the strainer is completely housed inside the spring pin, but does not mean that all of the strainer is housed inside the spring pin, e.g., if the edge of the strainer is outside the spring pin. It is intended to include cases.

According to the above-mentioned electromagnetic fuel injection valve, since the strainer is housed and integrated inside the spring pin,
There is no need to press-fit the strainer alone, only press-fitting of the spring pin is sufficient. For this reason, manufacturing costs can be reduced. Further, since it is not necessary to press-fit the spring pin alone, a metal collar for press-fitting and fixing the strainer is not required. For this reason, component costs can be reduced. Also, when adjusting the elastic force of the spring to adjust the dynamic flow rate, the strainer is housed inside the spring pin, so that a load that causes the strainer to deform is applied to the strainer. Can be prevented. For this reason, the deformation of the strainer is prevented, and the adjustment accuracy of the dynamic flow rate can be maintained.

According to another aspect of the present invention, there is provided an electromagnetic fuel injection valve having a substantially cylindrical body, a valve reciprocating in the body, and a spring located upstream of the valve. A spring pin in contact with the upstream end of the spring; and a strainer located upstream of the spring pin. The electromagnetic fuel injection valve is characterized in that the strainer is integrated with the spring pin, and deformation of the strainer is restrained by the spring pin. Here, “the deformation of the strainer is restrained by the spring pin” does not only mean a state in which the strainer is restrained so as not to deform at all, but the deformation amount is suppressed by the spring pin. It is intended to include the state in which

According to the electromagnetic fuel injection valve of the second aspect, the same effect as that of the electromagnetic fuel injection valve of the first aspect can be obtained. That is, since the spring pin and the strainer are integrated, the manufacturing cost and the component cost can be reduced as in the case of the first aspect. Further, when the strainer is pressed into the body, the deformation of the strainer is restrained by the spring pin, and the deformation is suppressed. Therefore, the adjustment accuracy of the dynamic flow rate can be maintained.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention described in the above-mentioned claims can be suitably implemented in the following forms. (Embodiment 1) In the electromagnetic fuel injection valve according to claim 1 or 2, the strainer and the spring pin are preferably fixed by welding or caulking (corresponding to the first and second embodiments). According to this aspect, since the strainer and the spring pin are securely fixed and integrated, it is possible to prevent the positional relationship between the strainer and the spring pin from being shifted due to the force acting when adjusting the dynamic flow rate. (Embodiment 2) In the electromagnetic fuel injection valve according to Claim 1 or 2, the strainer and the spring pin are provided with a contact portion that restricts the relative displacement of the strainer with respect to the spring pin in the axial direction. Is preferable (corresponding to the first embodiment and the second embodiment). According to this aspect, it is possible to prevent the relative positions in the axial direction from being shifted when the dynamic flow rate is adjusted. (Embodiment 3) In the electromagnetic fuel injection valve according to Claim 1 or 2, the spring pin has a fuel passage penetrating in the axial direction thereof, and a fuel inlet and a fuel outlet to the fuel passage. It is preferable that an opening is provided in the wall forming the fuel passage (corresponding to the first embodiment). According to this embodiment, the spring pin is easily deformed by the opening provided in the wall of the spring pin, and the press fit of the spring pin can be improved. (Embodiment 4) In the electromagnetic fuel injection valve according to Embodiment 3, it is preferable that the press-fit portion of the spring pin and the position of the opening are shifted in the axial direction (corresponding to the first embodiment). According to this embodiment, since the axial position of the press-fit portion and the portion where the opening is provided (the portion having low rigidity) is shifted, the portion having low rigidity is prevented from being excessively deformed. Therefore, the spring pin is prevented from being locally deformed, and the press-fitting property can be improved.

In the invention described in each of the claims and embodiments, the "body" includes a valve seat (so-called valve seat) in which a fuel injection hole and a sealing surface for sealing the fuel injection hole are formed; May be manufactured integrally with the body main body that forms the fuel flow path by guiding them, or may be manufactured separately. When manufactured in one piece, the step of fixing the body body and the valve seat body can be omitted.On the other hand, when the body is formed separately, the valve seat is fixed to the body body by adjusting the fixing position. The stroke can be fine-tuned.

[0013]

First Embodiment An electromagnetic fuel injection valve 1A according to a first embodiment of the present invention will be described with reference to FIG. FIG. 1 is a longitudinal sectional view of the electromagnetic fuel injection valve according to the first embodiment. First, a schematic configuration of the electromagnetic fuel injection valve according to the first embodiment will be described. An electromagnetic fuel injection valve 1A shown in FIG. 1 has a body 41 and a valve mechanism (a valve seat 4, a plate orifice 6, a valve 9, a valve 34, a core 34, a spring pin 32, a spring 36) provided inside the body 41. ), And a drive mechanism (such as the solenoid coil 18) provided on the outer periphery of the body 41 to drive the valve mechanism. The body main body 41 is a member formed in a cylindrical shape as shown in FIG. 1, and has a fuel passage formed therein. The body main body 41 includes a fuel connector portion 41B on the upstream side to be connected to a fuel pipe (not shown), and a valve body portion 41 on the downstream side for storing the valve 9 and the like.
A.

Next, a valve mechanism provided inside the body 41 will be described. A valve seat (valve seat) 4 having a columnar outer shape is press-fitted on the inner periphery on the downstream side (fuel injection hole side) of the body main body 41 described above. This valve seat 4 has a cylindrical hole 4 from behind.
D is open. This cylindrical hole 4D is
It functions as a guide for guiding 0 in the axial direction. Around this cylindrical hole 4D, fuel passages 4C extending in the axial direction are formed at three positions equidistant in the circumferential direction. A sheet surface (conical surface) 4A is formed downstream of the cylindrical hole 4D. The seat surface 4A functions as a seal surface that comes into contact with the ball 10 and closes the fuel injection hole 4B. The front end of the seat surface 4A opens to the front end surface of the valve seat 4, and this opening becomes the fuel injection hole 4B.

At the downstream end of the valve seat 4 described above,
The plate orifice 6 is fixed by a ring-shaped weld 8. The plate orifice 6 has a plurality of small holes 6A. The fuel injected from the fuel injection holes 4B of the valve seat 4 is atomized by the plurality of small holes 6A, and the injection direction is determined. A valve (valve) 9 is accommodated on the upstream side of the valve seat 4 so as to be able to reciprocate in the axial direction. The valve 9 includes, in order from the upstream side, an armature (movable iron core) 39 and a pipe (a cylindrical portion of the valve 9) 13 fixed to the armature 39.
And a ball (valve element) 10 connected to the pipe 13 by laser welding. Armature 3
9 is formed in a substantially hollow cylindrical shape by a magnetic material,
It is guided in the body main body 41 so as to be immovable in the radial direction and movable in the axial direction.

At the upstream side of the valve 9 manufactured as described above, a core (fixed iron core) 34 made of magnetic material as shown in FIG. A spring pin (adjuster) 32 is press-fitted and fixed inside the core 34. A spring (compression spring) 36 is accommodated between the spring pin 32 and the valve 9 in a compressed state. Therefore, the valve 9 is urged downstream by the restoring force of the spring 36, and the ball 10 abuts on the seat surface 4A of the valve seat 4 to close the fuel injection hole 4B.

A driving mechanism (such as the solenoid coil 18) for driving the above-described valve mechanism is provided on the outer periphery of the body main body 41. This solenoid coil 18
Attracts the valve 9 (armature 39) to the core 34 side by magnetic force generated by energization, separates the valve 9 from the seat surface 4A (that is, opens the valve 9), and injects fuel from the injection hole 4B. Let it. The solenoid coil 18 is positioned on the outer periphery of the body 41 by a cylindrical outer core 16 and a disk-shaped yoke 20. A connector 28 that supplies power to the solenoid coil 18 is provided upstream of the cylindrical outer core 16. Around the connector 28, the resin molding 22
Is provided. In FIG. 1, reference numeral 15 denotes an O-ring for keeping the connection between the electromagnetic fuel injection valve 1A and the engine side airtight. Reference numeral 24 denotes an electromagnetic fuel injection valve 1A.
An O-ring that keeps the connection between the airtight and the fuel pipe airtight.

Here, in the electromagnetic fuel injection valve 1A according to the first embodiment, the strainer 26 is fixed to the upstream side of the spring pin 32 and is integrated and pressed into the body 41. Hereinafter, the strainer 26 and the spring pin 32 will be described in detail with reference to FIG. FIG. 2 is a longitudinal sectional view of the vicinity of a strainer and a spring pin of the electromagnetic fuel injection valve according to the first embodiment. The strainer 26 is a metal filter that removes foreign substances contained in the fuel flowing from the fuel pipe. As shown in FIG. 2, the strainer 26 has a hemispherical (having a semicircular cross section) bottom surface 26D and a bottom surface 26D. A net portion 26E fixed to 26D, a side portion 26C extending upstream from an end of the bottom portion 26D, an outward flange portion 26B extending radially outward from an upstream end of the side portion 26C, It is constituted by an inward flange portion 26A obtained by bending the outer end of the orientation flange portion 26B radially inward. The outward flange portion 26B and the inward flange portion 26A
Has a substantially U shape when viewed as a whole.

The spring pin 32 is a hollow member formed into a substantially cylindrical shape by press deep drawing, and a fuel passage 32K is formed in the hollow portion to guide the fuel flowing from the upstream end to the downstream end. Have been. More specifically, a flange 32A to which the strainer 26 is attached is formed at the upstream end of the spring pin 32.
A fuel connector 41 is provided downstream of the flange 32A.
A second small diameter portion 32B having a diameter smaller than the inner diameter of B is continuously provided. On the downstream side of the second small diameter portion 32B,
A press-fit portion 32D having an outer diameter substantially equal to the inner diameter of the fuel connector portion 41B (a diameter slightly larger than the inner diameter of the fuel connector portion 41B) is provided via the flange portion 32C. On the downstream side of the press-fit portion 32D, a large-diameter portion 32E (the fuel connector portion 41B) having an outer diameter slightly smaller than the outer diameter of the press-fit portion 32D.
Is provided on the downstream side of the large-diameter portion 32E, and an inclined portion 32G whose diameter gradually decreases toward the downstream side is provided. The spring pin 3 extends from the large diameter portion 32E to the inclined portion 32G.
An opening 32F is formed in the second wall. This opening 32F is
The opening 32F is provided to improve the press fit of the spring pin 32 and communicates with the fuel passage 32K inside the spring pin 32 and the external space (the space between the fuel connector 41B and the spring pin 32). The fuel flows out of the fuel passage 32K into the external space through the fuel passage 32K. Further, a first small-diameter portion 32H to be press-fitted into the core 34 is provided on the downstream side of the inclined portion 32G, and a hole 32J as a fuel outlet is formed at the tip thereof. The hole 32J is formed to be smaller in diameter than the first small diameter portion 32H by an inward flange portion 32I extending radially inward from the tip of the first small diameter portion 32H. The downstream end surface of the inward flange portion 32I formed at the downstream end portion of the first small diameter portion 32H is a contact surface with which the upstream end surface of the spring 36 contacts. The first small diameter portion 32H described above
And the second small diameter portion 32B have substantially the same diameter.

Next, a process of assembling the spring pin 32 and the strainer 26 to the electromagnetic fuel injection valve 1A according to the first embodiment will be described. First, in order to fix the strainer 26 to the spring pin 32 shown in FIG. 2, the strainer 26 is inserted into the fuel passage 32K from the upstream opening of the spring pin 32. The strainer 26 is inserted and positioned in the axial direction until the outward flange portion 26B comes into contact with the flange portion 32A of the spring pin 32. Therefore, the outward flange portion 26B and the flange portion 32A correspond to the “contact portion” according to the second embodiment of the present invention. Then, the outward flange portion 26B of the strainer 26 and the flange portion 32A of the spring pin 32 are fixed by welding. As a result, the strainer 26 is housed inside the spring pin 32 and is integrated. Thus, the outward flange portion 26B
And the outward flange portion 32 </ b> A is brought into contact with each other and further fixed by welding, whereby the relative displacement of the strainer 26 in the axial direction with respect to the spring pin 32 is more strongly restricted.

Next, the spring pin 32 containing the strainer 26 therein is pressed into the body 41 from the upstream side so that the dynamic flow rate of the electromagnetic fuel injection valve 1A becomes a desired value. To adjust. That is, when the spring pin 32 is press-fitted and gradually moves downstream, the spring 36 interposed between the spring pin 32 and the armature 39 is gradually compressed. The compression distance of the spring 36 (the elastic force increases as the compression distance increases as long as it is within a certain distance) is adjusted so that the desired dynamic flow rate is obtained. Specifically, a jig for press-fitting is inserted into the body 41 from the upstream side, and the inward flange portion 26A of the strainer 26 is pressed to gradually move the spring pin 32 to the downstream side. When the dynamic flow rate becomes as follows, the pressing of the spring pin 32 is released. When the spring pin 32 moves downstream, the first small diameter portion 32H is pressed into the core 34, and the press-fit portion 32D of the spring pin 32 is pressed.
Is pressed into the body main body 41 (fuel connector portion 41B), so that even after the pressing by the jig is released, the spring pin 32 is fixed at that position and does not move.

As is clear from the above description, when the dynamic flow rate is adjusted (when the spring pin 32 is moving to the downstream side in the axial direction), the pressing force of the jig, A compressive force or the like from the body 41 acts on the press-fit portion 32D and the first small-diameter portion 32H. on the other hand,
After the dynamic flow rate is adjusted, the spring pin 32
Only the compressive force from the body 41 acts on the press-fit portion 32D and the first small diameter portion 32H. Therefore, in order to increase the adjustment accuracy of the dynamic flow rate, the flow path resistance of the spring pin 32 when the pressing force is applied for press-fitting and the flow path resistance of the spring pin 32 when the pressing force is not applied are required. It is desirable that they be the same. Here, in the electromagnetic fuel injection valve 1A according to the first embodiment, the strainer 26 is housed in the spring pin 32,
Even if the pressing force acts, it is prevented that an excessive force acts on the strainer 26, and the deformation thereof is suppressed. Further, the opening of the spring pin 32 to which the strainer 26 is attached is deformed by increasing the rigidity by providing the flange portion 32C and the second small diameter portion 32B (so-called reducing the diameter of the upper opening portion of the spring pin 32). It has become difficult. Therefore, even if the pressing force acts, the spring pin 3
The flow path resistance at the inflow portion of 2 (fuel flow path 32K) does not change.

An opening 32F is formed in the spring pin 32 in order to improve the press-fitting property. However, the position where the opening 32F is provided is a position that hardly affects the change in the flow path resistance. . That is, the spring pin 3
The large-diameter portion 32E and the inclined portion 32G are not located near the fuel inlet and the fuel outlet to the fuel cell 2, but are axially separated therefrom. Therefore, even if the rigidity is reduced in the portion where the opening 32F is provided, and the amount of deformation is increased by the pressing force, the flow path resistance is prevented from being largely changed by the deformation. In addition, this opening 32F is provided with the press-fit portion 3
Since the position is shifted in the axial direction with respect to 2D, the influence of the compressive force from the press-fit portion 32D can be reduced, and the opening 32F prevents the spring pin 32 from being excessively deformed. For the above reasons, in the electromagnetic fuel injection valve 1A of the present embodiment, the adjustment accuracy of the dynamic flow rate can be improved.

Further, according to the electromagnetic fuel injection valve 1A of the first embodiment, since the strainer 26 is housed and integrated inside the spring pin 32, there is no need to press-fit the strainer 26 alone. Only 32 press fits are needed. For this reason, manufacturing costs can be reduced. Further, since it is not necessary to press-fit the spring pin 32 alone, a metal collar for press-fitting and fixing the strainer 26 is not required. For this reason, component costs can be reduced. Further, since only the flange portions 26A and 26B of the strainer 26 extend outward from the flange portion 32A on the most upstream side of the spring pin 32, the jig is used to adjust the dynamic flow rate from the upstream side. Even if the pin 32 (strainer 26) is pressed, a load that causes deformation of the strainer 26 is applied.
6 can be prevented. For this reason, strainer 2
Since the deformation of No. 6 does not occur, the adjustment accuracy of the dynamic flow rate can be maintained.

Next, an electromagnetic fuel injection valve according to a second embodiment of the present invention will be described with reference to FIGS. FIG.
FIG. 4 is a longitudinal sectional view of an electromagnetic fuel injection valve according to a second embodiment, and FIG. 4 is a longitudinal sectional view near the strainer and a spring pin. Note that members having the same functions as the members of the electromagnetic fuel injection valve 1A according to the first embodiment are denoted by the same reference numerals, and description thereof will be omitted. The electromagnetic fuel injection valve 1B according to the second embodiment shown in FIG. 3 mainly includes the shapes of the strainer 27 and the spring pin 33 and the structure for assembling them. This is different from the fuel injection valve 1A. Specifically, as shown in FIG. 4, the strainer (filter) 27 is a hemisphere (the cross section is a semicircle).
, A net portion 27C fixed to the bottom surface portion 27B, and a side surface portion 27A extending upstream from an end of the bottom surface portion 27B. No net portion is provided on the side surface portion 27A.

On the upstream side of the spring pin 33, there is formed a caulking portion 33A for integrally fixing the strainer 27 by caulking. The swaging portion 33A is provided at the upstream end 33 of the spring pin 33 as described later.
It is formed by caulking B. This caulking part 3
A press-fit portion 33C is formed from 3A via a bent portion 33I. The press-fit portion 33C has an outer diameter substantially equal to the inner diameter of the fuel connector portion 42B (a diameter slightly larger than the inner diameter of the fuel connector portion 41B). On the downstream side of the press-fit portion 33C, a large-diameter portion 33D whose outer diameter is slightly smaller than the outer diameter of the press-fit portion 33C (diameter substantially equal to the inner diameter of the fuel connector portion 42B)
Is provided. A flange 33E extending radially inward from the downstream end of the large diameter portion 33D and a small diameter portion 33F extending downstream from the flange 33E are provided. An inward flange portion 33G extending radially inward is provided from the downstream end portion of the small diameter portion 33F, and the inward flange portion 33G has an inward flange portion 33G.
H is formed. The downstream end surface of the inward flange portion 33G of the spring pin 33 is in contact with the upstream end portion of the spring 37.

Next, a process of assembling the spring pin 33 and the strainer 27 to the electromagnetic fuel injection valve 1B according to the second embodiment will be described. First, the spring pin 33
The strainer 27 is inserted from the opening formed by the end portion 33B located on the upstream side of the spring pin 32 to a position where the side surface portion 27A comes into contact with the press-fit portion 33C of the spring pin 32.
Then, the end portion 33B of the spring pin 33 is swaged from the upstream side using a jig, and the swaged portion 33A and the bent portion 33I are formed.
To form The caulked portion 33A and the spring pin 33
The side portion 27A of the strainer 27 is sandwiched and fixed by the press-fit portion 33C. As a result, the upstream end of the side surface portion 27A and the bent portion 33I come into contact with each other, and the relative displacement of the two in the axial direction (the displacement of the strainer 27 to the upstream side) is restricted. Therefore, the upstream end of the side portion 27A and the bent portion 3
3I is equivalent to the "contact part" in the form 2 in the embodiment of the invention. As a result, the strainer 27 is housed inside the spring pin 33 and becomes an integrated state. Thus, the upstream end 33B of the strainer 27
By forming the caulked portion 33A and abutting the upstream end portion of the side surface portion 27A and the bent portion 33I, the relative displacement of the strainer 27 in the axial direction with respect to the spring pin 33 is more firmly regulated. .

Next, the spring pin 33 in which the strainer 27 is accommodated is pressed into the body 41 from the upstream side. When the spring pin 33 is gradually moved downstream by the press-fitting, as a result, the spring 37 in contact with the inward flange portion 33G of the spring pin 33 is gradually compressed. The distance by which the spring 37 is compressed is adjusted so that a desired dynamic flow rate is obtained.

According to the electromagnetic fuel injection valve 1B of the second embodiment, as in the first embodiment, the strainer 27 is housed and integrated inside the spring pin 33, thereby reducing the manufacturing cost and the component cost. Further, since the entire strainer 27 including the end portion is housed and integrated inside the spring pin 33, the spring pin 33 can be adjusted from the upstream side with a jig to adjust the dynamic flow rate. Even if the (strainer 27) is pressed, a load that causes deformation of the strainer 27 is applied.
7 can be prevented. For this reason, strainer 2
Since the deformation of 7 does not occur, the adjustment accuracy of the dynamic flow rate can be maintained. Furthermore, since the spring pin 33 is not provided with an opening as shown in the first embodiment on the side surface, the dynamic flow rate can be adjusted without taking into account the deformation of the fuel passage, so that the adjustment is easy. , And fine adjustment can be performed with high accuracy.

As described above, the electromagnetic fuel injection valve according to the present invention has been described using some preferred embodiments. However, the present invention is not limited to the above embodiments.
Various modifications and improvements can be made based on the knowledge of those skilled in the art.

For example, in this embodiment, the spring pins 3
Although the example in which the strainers 26 and 27 are housed and integrated inside the 2 or 33 respectively has been described, the invention described in claim 2 of the present invention houses the strainer 26 inside the spring pin 32. It is not limited to the case.
For example, the strainer has a cap shape having a side surface portion and a net portion, and the side surface portion is located on the outer side portion of the spring pin, and the net portion contacts the upstream end of the spring pin ( That is, the spring pin may be formed with a strainer). Even in this case, the deformation of the strainer is restrained by the spring pin.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of an electromagnetic fuel injection valve according to a first embodiment.

FIG. 2 is a longitudinal sectional view of the vicinity of a strainer and a spring pin according to the first embodiment.

FIG. 3 is a longitudinal sectional view of an electromagnetic fuel injection valve according to a second embodiment.

FIG. 4 is a longitudinal sectional view of the vicinity of a strainer and a spring pin according to a second embodiment.

FIG. 5 is a longitudinal sectional view (1) of an electromagnetic fuel injection valve according to the related art.

FIG. 6 is a longitudinal sectional view (2) of an electromagnetic fuel injection valve according to the related art.

FIG. 7 is a perspective view of a strainer of the electromagnetic fuel injection valve shown in FIG. 6;

[Explanation of symbols]

1A, B: electromagnetic fuel injection valve 4: valve seat (valve seat), 4A: seat surface (corresponding to sealing surface), 4B: fuel injection hole, 4C: fuel passage, 4
D: cylindrical hole 6: plate orifice, 6A: multiple small holes 8: welded part 9: valve (valve) 10: ball (corresponding to valve body) 13: pipe (tube part of valve) 15: O-ring ( (Electromagnetic fuel injection valve and engine side) 16: Outer core 18: Solenoid coil 20: Yoke 22: Resin molded body 24: O-ring (Electromagnetic fuel injection valve and fuel pipe side) 26, 27: Strainer (filter) 26A: Inward flange portion, 26B: outward flange portion, 26C: side portion, 26D: bottom portion, 26E: net portion 27A: side portion, 27B: bottom portion, 27C: net portion 28: connector 32, 33: spring pin ( Adjuster) 32A: flange portion, 32B: second small diameter portion, 32C: flange portion, 32D: press-fit portion, 32E: large diameter portion, 32F:
Opening, 32G: inclined portion, 32H: first small diameter portion, 32I:
Inward flange portion, 32J: hole portion, 32K: fuel passage 33A: caulked portion, 33B: upstream end portion, 33C: press-fit portion, 33D: large diameter portion, 33E: flange portion, 33F:
Small diameter part, 33G: Inward flange part, 33H: Hole part, 3
3I: bent portion, 33G: inward flange portion 33G 34, 35: core (fixed iron core) 36, 37: spring (compression spring) 39: armature (movable iron core) 41, 42: body body, 41A, 42A: valve body Parts, 41B, 42B: fuel connector part

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification FI FI Theme Court ゛ (Reference) F02M 61/16 F02M 69/00 320Q (72) Inventor Motoyuki Suzuki 1-1-1 Kyowacho, Obu City, Aichi Prefecture 1 Ai San Kogyo Co., Ltd. (72) Inventor Kazuaki Koyanagi 1-1, Kyowa-cho, Obu City, Aichi Prefecture Ai San Kogyo Co., Ltd. F-term (reference) 3G066 AD07 BA56 BA58 BA61 BA67 CC01 CC06U CC15 CD11 CE22

Claims (2)

[Claims] 1. A substantially cylindrical body, a valve reciprocating in the body, a spring positioned upstream of the valve, a spring pin in contact with an upstream end of the spring, and a spring pin. An electromagnetic fuel injection valve, comprising: a strainer positioned on the upstream side; wherein the strainer is housed and integrated inside the spring pin. 2. A substantially cylindrical body, a valve reciprocating in the body, a spring positioned upstream of the valve, a spring pin in contact with an upstream end of the spring, and a spring pin. A strainer positioned upstream, wherein the strainer is integrated with the spring pin and deformation of the strainer is restrained by the spring pin.