JPH10159673A - Injection valve - Google Patents

Injection valve

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Publication number
JPH10159673A
JPH10159673A JP32285796A JP32285796A JPH10159673A JP H10159673 A JPH10159673 A JP H10159673A JP 32285796 A JP32285796 A JP 32285796A JP 32285796 A JP32285796 A JP 32285796A JP H10159673 A JPH10159673 A JP H10159673A
Authority
JP
Japan
Prior art keywords
needle
piezoelectric element
piston
injection valve
damper chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP32285796A
Other languages
Japanese (ja)
Other versions
JP3680461B2 (en
Inventor
Takayuki Arai
Takashi Fukuda
Masahiko Katsu
雅彦 勝
隆 福田
孝之 荒井
Original Assignee
Nissan Motor Co Ltd
日産自動車株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd, 日産自動車株式会社 filed Critical Nissan Motor Co Ltd
Priority to JP32285796A priority Critical patent/JP3680461B2/en
Publication of JPH10159673A publication Critical patent/JPH10159673A/en
Application granted granted Critical
Publication of JP3680461B2 publication Critical patent/JP3680461B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Abstract

(57) [Problem] To suppress variation in injection amount in an injection valve using a piezoelectric element as an actuator. A needle (2) that moves in an axial direction to open and close an injection port (1b), and a needle (2) that extends by an applied voltage and extends.
, A piston 16 coupled to the base end of the piezoelectric element 10, a spring 17 biasing the piston 16 in a direction to compress the piezoelectric element 10, and a piston 16. A damper chamber 27 and a throttle passage 25 that imparts resistance to fuel flowing into and out of the damper chamber 27 are provided.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve structure using a piezoelectric element as an actuator, which is applied to an engine fuel injection valve or the like.

[0002]

2. Description of the Related Art Some fuel injection valves and the like provided in an automobile engine open a needle (valve element) using a laminated piezoelectric element (piezo element) that expands in accordance with an applied voltage. By driving the needle by the piezoelectric element, the high-speed response of the fuel injection valve is improved, and the output is increased. In addition, it is possible to stably inject a small amount of fuel, thereby reducing fuel consumption.

Conventionally, as this type of fuel injection valve, for example, there is one as shown in FIG. (Japanese Unexamined Patent Publication No.
No. 3, reference).

[0004] To explain this, the nozzle body 5
1, the needle 52 is slidably housed. A fuel chamber 53 is defined inside the nozzle body 51 around the needle 52. A nozzle 51b is opened at the tip of the nozzle body 51, and the nozzle 51b is opened and closed by a needle 52.

Fuel fed from a fuel injection pump (not shown) is introduced into a fuel chamber 53 from a fuel inlet 63 through a fuel passage 62, and the injection port 5 is moved with the lift of the needle 52.
1b.

A coil-shaped spring 54 for urging the needle 52 in the valve closing direction is provided.

[0007] A piezoelectric element 60 for driving the needle 52 in the valve opening direction is provided. The piezoelectric element 60 expands against the spring 54 when a voltage is applied via the lead wire 68, and lifts the needle 62 via the retainer 67.

[0008]

However, in such a conventional fuel injection valve, a metal needle 5 is required.
Due to the structure in which the piezoelectric elements 60 having different linear expansion coefficients are interposed between the nozzle body 51 and the nozzle body 51, when the temperature of the fuel injection valve changes, a thermal expansion difference occurs between the nozzle body 51 and the piezoelectric element 60, As a result, there is a problem that the lift amount of the needle 52 changes and the desired fuel injection amount cannot be obtained.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has as its object to suppress variations in injection amount in an injection valve using a piezoelectric element as an actuator.

[0010]

According to a first aspect of the present invention, there is provided an injection valve for injecting a pressurized fluid guided from a fluid passage;
A needle that moves in the axial direction to open and close the nozzle, a piezoelectric element that expands by an applied voltage and presses the needle in the axial direction, a piston that is coupled to the base end of the piezoelectric element, and allows the piston to slide. A casing to be accommodated, biasing means for biasing the piston in a direction to compress the piezoelectric element, a damper chamber defined between the piston and the casing, and a throttle for imparting resistance to the fluid flowing into and out of the damper chamber And a passage.

According to a second aspect of the present invention, in the injection valve according to the first aspect, the resistance which the throttle passage imparts to the fluid flowing into and out of the damper chamber is controlled by the pressure drop of the damper chamber during the valve opening period of the needle. ΔP is 1 of the maximum pressure difference of the damper chamber.
It was set to be within 0%.

According to a third aspect of the present invention, in the injection valve according to the first or second aspect, a communication passage connecting the fluid passage and the throttle passage is formed in the casing.

According to a fourth aspect of the present invention, in the injection valve according to the third aspect of the present invention, the injection valve includes a bolt screwed to the casing, and the bolt forms a throttle passage connecting the damper chamber and the communication passage.

According to a fifth aspect of the present invention, in the injection valve according to any one of the first to fourth aspects, the means for urging the piston in a direction to compress the piezoelectric element is coaxial with the piston. , A rear end member for supporting one end of the flat spring, and means for adjusting a screwing position of the rear end member with respect to the casing.

According to a sixth aspect of the present invention, there is provided the injection valve according to any one of the first to fifth aspects, wherein a needle for opening / closing the injection port by opening / closing the injection port while being in contact with / separating from the seat surface where the injection port is opened. The apparatus includes a means for urging in the valve direction, and a piezoelectric element which expands by an applied voltage and drives the needle directly in the valve closing direction.

[0016]

In the injection valve according to the first aspect, by intermittently applying a voltage to the piezoelectric element, the needle is moved in the axial direction by expanding and contracting the piezoelectric element.
Open and close the spout.

The piston attempts to change the volume of the damper chamber as the piezoelectric element expands and contracts when the nozzle is opened and closed. However, since the throttle passage imparts resistance to the fluid flowing in and out of the damper chamber, the displacement of the piston is suppressed. The base end of the piezoelectric element is held as a fixed end.

On the other hand, a difference in thermal expansion between the needle, the casing, and the piezoelectric element caused by a change in the environmental temperature of the injection valve is absorbed by a piston coupled to a base end of the piezoelectric element, which expands and contracts the damper chamber to be displaced. Thus, the desired injection amount can be obtained while keeping the needle lift constant.

In the injection valve according to the second aspect of the present invention, the resistance applied by the throttle passage to the fluid flowing into and out of the damper chamber is determined by reducing the pressure drop ΔP of the damper chamber during the valve opening period of the needle by the maximum pressure difference of the damper chamber by 10%. %, The displacement of the piston during the valve opening period of the needle is sufficiently suppressed, and the base end of the piezoelectric element is held as a fixed end. As a result, it is possible to stably inject a small amount of fuel, thereby reducing fuel consumption.

In the injection valve according to the third aspect of the present invention, the communication passage connecting the fluid passage and the throttle passage is formed in the casing, so that the fluid flowing into and out of the damper chamber is guided from the fluid passage, thereby simplifying the structure. .

In the injection valve according to the fourth aspect, by forming the throttle passage in the bolt screwed into the casing, it is possible to change the size of the throttle passage by replacing the bolt, thereby improving productivity and The maintainability is improved.

According to a fifth aspect of the present invention, as a means for biasing the piston in a direction to compress the piezoelectric element, a spring arranged concentrically with the piston is uniformly distributed in the circumferential direction with respect to the piston. Since the force is applied, the piston is smoothly moved without biasing the piston in the eccentric direction, and stable operability is secured.

By adjusting the screwing position of the rear end member with respect to the casing, the biasing force of the flat spring can be easily adjusted.

In the injection valve according to the sixth aspect, when a voltage is applied to the piezoelectric element, the piezoelectric element expands to bring the needle closer to the seat surface and close the injection port.

When the voltage applied to the piezoelectric element is cut off, the urging means causes the needle to follow the contraction of the piezoelectric element, separates the needle from the seating surface, and opens the injection port.

Since the direction of displacement of the piezoelectric element coincides with the direction of displacement of the needle, it is possible to arrange the piezoelectric element and the needle in series and drive the needle by bringing the needle into contact with the piezoelectric element. As a result, a mechanism for inverting the driving force of the piezoelectric element and transmitting it to the needle is not required, and the structure can be simplified.

[0027]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to a fuel injection valve provided in a direct injection type spark ignition engine will be described below with reference to the accompanying drawings.

As shown in FIGS. 1 and 2, the nozzle body 1
The needle 2 is slidably housed inside the cylinder 9. Needle 2 inside nozzle body 1 and cylinder 9
Around the fuel chamber (fluid chamber) 3 is defined. A nozzle 1b is opened at the tip of the nozzle body 1, and the nozzle 1b is opened and closed by a needle 2.

Fuel pumped from a fuel injection pump (not shown) is introduced into the fuel chamber 3 from a fuel inlet 13 through a fuel passage (fluid passage) 12, and is injected from the injection port 1b with the lift of the needle 2. The nozzle body 1 faces the combustion chamber from the combustion chamber ceiling wall of the engine, and sprays fuel spray from the injection port 1b toward the crown of the piston.

Inside the nozzle body 1, a seating surface 1a is recessed in a conical shape around an injection port 1b. On the other hand, a seat portion 2 a protrudes in a conical shape from the tip of the needle 2. Seat part 2
When a is seated on the seating surface 1a, the injection port 1b is closed. By separating the seat portion 2a from the seating surface 1a,
The nozzle 1b is opened.

The support portion 2b protrudes from the middle of the needle 2 in the outer diameter direction, and slides into contact with the cylindrical inner wall surface of the nozzle body 1 so that the seat portion 2a is coaxial with the seat surface 1a. invite. Support part 2b and nozzle body 1
A passage through which the fuel flows is formed between the inner wall surfaces.

The needle 2 has a piston 2c at its proximal end.
Are formed to project in an annular shape. An O-ring 5 is interposed in an annular groove formed on the outer periphery of the piston portion 2c. O-ring 5
Slides on the cylindrical inner wall surface of the cylinder 9 to seal the fuel chamber 3. O-ring 5 in annular groove
A backup ring 6 is interposed behind the O-ring so that the O-ring 5 does not protrude from the annular groove due to hydraulic pressure.

A spring 4 for urging the needle 2 in the valve opening direction is provided. The flat spring 4 is interposed between the piston portion 2 c of the needle 2 and the nozzle body 1 in a compressed state, and is arranged coaxially with the needle 2. This allows
The flat spring 4 separates the seat portion 2a of the needle 2 from the seat surface 1a by its elastic restoring force.

A piezoelectric element 10 for pressing the needle 2 in the valve closing direction is provided in the cylinder 9. This piezoelectric element 10
Is applied with a voltage through the lead wire 23,
The needle 2 instantaneously extends in the sliding direction, and the seat portion 2a is seated on the seating surface 1a. On the other hand, the piezoelectric element 10 contracts instantaneously by interrupting the voltage applied thereto and short-circuiting between both terminals of the piezoelectric element 10, and the needle 2
The seat portion 2a moves away from the seat surface 1a in the axial direction by the combined force of the fuel pressure and the biasing force of the spring 4.
The force by which the piezoelectric element 10 presses the needle 2 in the valve closing direction is:
The pressure is set to be larger than the sum of the fuel pressure of the fuel chamber 3 and the biasing force of the spring 4.

In the piezoelectric element 10, a plurality of disk-shaped piezoelectric elements (piezo elements) are stacked with a disk-shaped internal electrode plate interposed therebetween. The plate thickness of the piezoelectric simple substance is increased by applying a voltage and storing electric charge, and the plate thickness is reduced by cutting off the voltage and short-circuiting between both terminals.

An end plate 11, a ball 8 and a shim 7 are interposed between the driving end (tip) of the piezoelectric element 10 and the needle 2.

An end plate 11 is connected to the driving end of the piezoelectric element 10. The ball 8 is interposed between the end plate 11 and the needle 2. A pair of concave portions that are concave in a spherical shape are formed on the base plate of the end plate 11 and the needle 2. The ball 8 is sandwiched between the concave portions.

The shim 7 is formed in a disk shape. The shim 7 is interposed between the base end of the needle 2 and the cylinder 9 and regulates the axial movement of the needle 2. That is, the piezoelectric element 10
Is set to be larger than the full lift A of the needle 2, the full lift A of the needle 2 is determined by the thickness of the shim 7.

The lead wire 23 is taken out from the hole 22 of the cylinder 9, and the space between the hole 22 and the lead wire 23 is sealed via a seal 24.

The lead wire 23 extends to a drive circuit (not shown). A control unit (not shown) calculates a fuel injection amount according to an intake air amount and a rotation speed of the engine.
A pulse signal corresponding to the fuel injection amount calculated by the control unit is generated by a pulse generator, and a voltage corresponding to the pulse signal is applied to the piezoelectric element 10 via a drive circuit.

A piston 16 is connected to the base end of the piezoelectric element 10 and is provided to be displaceable with respect to the cylinder 9.

Rear end member 2 screwed into the open end of cylinder 9
0 is provided. A flat spring 17 is interposed between the front end of the rear end member 20 and the piston 16 in a compressed state. The elastic restoring force of the Sarah spring 17 is set to be greater than the elastic restoring force of the Sarah spring 4, and the driving end of the piezoelectric element 10 is pressed against the base end of the needle 2 via the ball 8 by the elastic restoring force of the Sarah spring 17. 2a is pressed against the seating surface 1a.

The rear end member 20 has a nut 21 screwed thereto.
The elastic restoring force of each of the springs 17 and 4 is adjusted by changing the screwing position with respect to the cylinder 9 through the screw.

A damper chamber 27 is defined between the rear end member 20 and the piston 16. Since the damper chamber 27 communicates with the fuel chamber 3 via the throttle passage 25 as described later, the volume of the damper chamber 27 is kept substantially constant even when the piezoelectric element 10 instantaneously expands and contracts. For this reason, the base end of the piezoelectric element 10 is held as a fixed end via the piston 16.

An O-ring 15 and a backup ring 14 are interposed in an annular groove formed on the outer periphery of the piston 16. An O-ring 18 and a backup ring 19 are interposed in an annular groove formed on the outer periphery of the rear end member 20. The damper chamber 27 is hermetically sealed via the O-rings 15 and 18.

The damper chamber 27 communicates with the fuel chamber 3 via a communication passage 26 formed in the cylinder 9 and a throttle passage 25.

The communication passage 26 has two through holes 26a, 2a, 2b formed by drilling a cylindrical wall of the cylinder 9.
6b. One end of the through hole 26a communicates with the fuel chamber 3, and a plug 28 is interposed at the open end of the through hole 26b and is closed.

The cylinder 9 is provided with a bolt 31 that is screwed through the communication passage 26, and the bolt 31 forms a throttle passage 25 that connects the communication passage 26 and the damper chamber 27.

As shown in FIGS. 3 and 4, the bolt 31 has a screw portion 32 screwed to the cylinder 9 and a head portion 33 joined to the outer wall of the cylinder 9. It is fastened to the screw hole of the cylinder 9 via a matching tool.

An annular groove 35 is formed on the outer periphery of the screw portion 32. The throttle passage 25 has a through hole 36 opening to the annular groove 35.
Is defined by a through hole 37 communicating with the through hole 36 and opening at the end thereof.

FIG. 5 is a model diagram of the throttle passage 25. Assuming that the diameter of the throttle passage 25 is d, the length is r, the pressure of the damper chamber 27 is P1, and the pressure of the fuel chamber 3 is P2, the throttle passage 25
Is calculated by the following equation.

Q = C × A × (2 × ΔP / ρ) 1/2 (1) where C: [(Re / 64) / (r / d + 0.4)
95)] 1/2 A: Restriction cross-sectional area ΔP: Pressure difference (= P1-P2) ρ: Density Re: Reynolds number (= vd / υ) v: Average flow velocity inside the restrictor :: Dynamic viscosity coefficient FIG. Elapsed time for contracting element 10 (ejection period)
FIG. 4 is a characteristic diagram showing a relationship between the pressure difference ΔP calculated using the equation (1) and a pressure difference of about 20 due to the displacement of the piezoelectric element 10.
kg / m 2 and the displacement of the piezoelectric element 10 is reduced to about 50 μm.
When the diameter d of the throttle passage 25 is 0.5 mm or less,
Preferably, the pressure difference ΔP is set to about 2 mm / m 2 until the elapsed time reaches 10 ms by setting the pressure difference to about 0.3 mm.
It can be suppressed to the extent. Therefore, the maximum injection period is about 10
In the case of a fuel injection valve having a length of 0.5 ms, the diameter d of the throttle passage 25 is set to 0.5 mm or less and about 0.3 mm to reduce the pressure drop ΔP of the damper chamber 27 during the valve opening period of the needle 2. The pressure difference is within 10% of the maximum pressure difference in the chamber 27, the volume of the damper chamber 27 hardly changes, and the base end of the piezoelectric element 10 can be held.

The configuration is as described above. Next, the operation will be described.

FIGS. 1 and 2 show the fuel injection valve in a state before the engine is started. The piezoelectric element 10 is extended when a voltage is applied, and the seat portion 2a of the needle 2 is connected to the seating surface 1.
a. In this state, the fuel injection pump (not shown) is driven by the electric motor, and the pressure in the fuel chamber 3 and the damper chamber 27 is increased to about 5 MPa.

When the engine is stopped, the driving end of the piezoelectric element 10 is pressed against the base end of the needle 2 via the ball 8 by the elastic restoring force of the spring 17, so that the seat portion 2a of the needle 2 is seated on the seat surface 1a. Thus, fuel leakage is prevented.

The valve opening operation of the fuel injection valve at the start of the engine and after the start is performed by cutting off the voltage applied by the piezoelectric element 10 in synchronization with the engine rotation and short-circuiting both terminals of the piezoelectric element 10. The needle 2 contracts instantaneously, and the needle 2 is moved in the axial direction by the combined force of the fuel pressure of the fuel chamber 3 and the biasing force of the spring 4, so that the seat 2a is moved to the seat surface 1a.
Move away from When the seat portion 2a separates from the seating surface 1a, the high-pressure fuel in the fuel chamber 3 is injected into the combustion chamber of the engine through the injection port 1b.

The valve closing operation of the fuel injection valve is extended by applying a voltage to the piezoelectric element 10 in synchronization with the rotation of the engine, and the needle 2 matches the fuel pressure of the fuel chamber 3 with the biasing force of the spring 4. The seat portion 2a moves in the axial direction against the force and approaches the seating surface 1a to be seated. When the seat portion 2a approaches the seating surface 1a and is seated, the injection port 1b is closed, and fuel injection is stopped.

By the way, the spring 17 presses the needle 2 through the piston 16 against the seat surface 1a. Therefore, when a change occurs in the ambient temperature of the fuel injection valve, the thermal expansion difference generated between the needle 2, the casing 9 and the piezoelectric element 10 is caused by the piston 16 coupled to the base end of the piezoelectric element 10 causing the damper chamber 27 to expand and contract. The end plate 11 of the piezoelectric element 10 is held at a position where the nidol 2 closes the injection port 1b.

The resistance applied by the throttle passage 25 to the fluid flowing into and out of the damper chamber 27 is, as described above, the drop pressure ΔP of the damper chamber 27 during the valve opening period of the needle being 10% of the maximum pressure difference of the damper chamber 27. By setting so as to be within, the displacement amount of the piston 16 in the short-circuit valve opening operation of the needle 2 is sufficiently suppressed, and the base end of the piezoelectric element 10 is held. As a result, it is possible to stably inject a small amount of fuel, thereby reducing fuel consumption.

On the other hand, by forming a communication passage 26 communicating the fuel chamber 3 and the throttle passage 25 in the casing 9, the fluid flowing into and out of the damper chamber 27 is guided from the fuel passage 13,
The structure is simplified.

Further, a bolt 31 screwed to the casing 9
By forming the throttle passage 25 in the above, it is possible to change the size of the throttle passage 25 by exchanging the bolt 9, thereby improving the productivity and the maintainability.

The piston 1 moves in the direction to compress the piezoelectric element 10.
As means for biasing the piston 6, the spring 16 arranged concentrically with the piston 16 applies a force uniformly distributed in the circumferential direction to the piston 16, so that the piston 16 is not biased in the eccentric direction. In addition, the movement of the piston 16 is made smooth, and stable operability is secured.

By adjusting the screwing position of the rear end member 20 with respect to the casing 9, the urging force of the spring 17 can be easily adjusted.

When the valve is opened, the displacement of the piezoelectric element 10 is set to be larger than the full lift of the needle 2, so that the needle 2 moves by a predetermined full lift while sitting on the shim 7. Therefore, when the needle 2 is fully lifted, a constant fuel flow path is defined between the seat portion 2a of the needle 2 and the seating surface 1a, and a fuel injection rate determined by the fuel pressure guided to the fuel chamber 3 is obtained.

When the valve is opened, the piezoelectric element 10 comes into contact with the needle 2 via the ball 8, so that the movement of the needle 2 can be smoothly performed without being affected by the dimensional error of the piezoelectric element 10 or the inclination of the piezoelectric element 10. Thus, stable operability is ensured. Further, since no uneven load is applied to the piezoelectric element 10, the durability of the piezoelectric element 10 can be improved.

In the fuel injection valve, since the direction of displacement of the piezoelectric element 10 and the direction of displacement of the needle 2 match, the piezoelectric element 1
0 and the needle 2 are arranged in series, and the piezoelectric element 10 can be driven by bringing the needle 2 into contact therewith. As a result,
A mechanism for transmitting the driving force of the piezoelectric element 10 to the needle 2 by reversing the driving force is not required, and the structure is simplified.

In this embodiment, the structure is such that the displacement of the piezoelectric element 10 is directly transmitted to the needle 2. However, the structure may be such that the displacement of the piezoelectric element 10 is transmitted to the needle 2 after being enlarged or reduced.

[Brief description of the drawings]

FIG. 1 is a sectional view of a fuel injection valve showing an embodiment of the present invention.

FIG. 2 is a sectional view of the fuel injection valve.

FIG. 3 is a front view of the bolt.

FIG. 4 is a side view of the bolt.

FIG. 5 is a model diagram of a throttle passage.

FIG. 6 is a characteristic diagram showing a relationship between an elapsed time for contracting a piezoelectric element and a pressure difference ΔP.

FIG. 7 is a sectional view of a fuel injection valve showing a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Nozzle body 1a Seat surface 1b Injection port 2 Needle 2a Seat part 3 Fuel chamber 4 Sara spring 5 O-ring 6 Backup ring 7 Shim 8 Ball 9 Cylinder 10 Piezoelectric element 11 End plate 12 Fuel inlet 13 Fuel passage 14 Backup ring 15 O ring 16 Piston 17 Sarah spring 18 O-ring 19 Sarah spring 20 Rear end member 23 Lead wire 25 Throttle passage 27 Damper chamber 31 Bolt

Claims (6)

[Claims]
1. A nozzle for injecting a pressurized fluid guided from a fluid passage, a needle which moves in an axial direction to open and close the nozzle, and a piezoelectric element which is extended by an applied voltage and presses the needle in an axial direction. A piston coupled to the base end of the piezoelectric element, a casing for slidably accommodating the piston, biasing means for biasing the piston in a direction to compress the piezoelectric element, and a gap between the piston and the casing. An injection valve, comprising: a damper chamber that is formed; and a throttle passage that imparts resistance to fluid flowing into and out of the damper chamber.
2. The resistance applied by the throttle passage to the fluid flowing into and out of the damper chamber is set so that the pressure drop ΔP of the damper chamber during the valve opening period of the needle is within 10% of the maximum pressure difference of the damper chamber. The injection valve according to claim 1, wherein:
3. The injection valve according to claim 1, wherein a communication passage connecting the fluid passage and the throttle passage is formed in the casing.
4. The injection valve according to claim 3, further comprising a bolt screwed to the casing, wherein the bolt has a throttle passage connecting the damper chamber and the communication passage.
5. A means for urging a piston in a direction to compress the piezoelectric element, a spring arranged concentrically with the piston, a rear end member supporting one end of the spring, and a rear end member with respect to the casing. The injection valve according to any one of claims 1 to 4, further comprising: means for adjusting a screwing position.
6. A needle for opening and closing a nozzle by contacting and separating the nozzle with an open seat surface, means for urging the needle in a valve opening direction, and extending directly by an applied voltage to directly close the needle. The injection valve according to any one of claims 1 to 5, further comprising: a piezoelectric element that is driven in a direction.
JP32285796A 1996-12-03 1996-12-03 Injection valve Expired - Lifetime JP3680461B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP32285796A JP3680461B2 (en) 1996-12-03 1996-12-03 Injection valve

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP32285796A JP3680461B2 (en) 1996-12-03 1996-12-03 Injection valve

Publications (2)

Publication Number Publication Date
JPH10159673A true JPH10159673A (en) 1998-06-16
JP3680461B2 JP3680461B2 (en) 2005-08-10

Family

ID=18148388

Family Applications (1)

Application Number Title Priority Date Filing Date
JP32285796A Expired - Lifetime JP3680461B2 (en) 1996-12-03 1996-12-03 Injection valve

Country Status (1)

Country Link
JP (1) JP3680461B2 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1391606A1 (en) * 2002-08-20 2004-02-25 Siemens VDO Automotive S.p.A. Metering device with adjustable flow rate and method for setting a flow rate of a metering device
JP2008534859A (en) * 2005-04-06 2008-08-28 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツングRobert Bosch Gmbh Fuel injection valve
US7886993B2 (en) 2002-04-04 2011-02-15 Siemens Aktiengesellschaft Injection valve

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7886993B2 (en) 2002-04-04 2011-02-15 Siemens Aktiengesellschaft Injection valve
EP1391606A1 (en) * 2002-08-20 2004-02-25 Siemens VDO Automotive S.p.A. Metering device with adjustable flow rate and method for setting a flow rate of a metering device
JP2008534859A (en) * 2005-04-06 2008-08-28 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツングRobert Bosch Gmbh Fuel injection valve

Also Published As

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