JP2012160479A - Ignition device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an ignition device with excellent ignitability and durability for causing ignition by injecting plasma-state gas in an engine.SOLUTION: In an ignition device 1, a discharge space 140 is blocked by a center electrode 110, an approximate tubular insulator 120 extending downward beyond its lower end, and a ground electrode 130 provided with an opening 131 communicated with its opening. A high voltage is applied and a large current is supplied to the discharge space 140, and gas in the discharge space 140 is made into a plasma state and injected in an engine combustion chamber 400 for causing ignition. A rotation providing mechanism provides a rotation force toward a center from an outer periphery of an airflow to a flow of the gas emitted from the discharge space 140. An opening of the ground electrode 130 is flush with and communicated with a lower bottom opening of the insulator 120 to become a first opening 131. A second opening 132 has a rotation providing space 141 projecting toward its tip, and blocked by a tubular peripheral wall 133 surrounding the first opening 131.

Description

  The present invention relates to an improvement in ignitability of an ignition device used for ignition of an internal combustion engine.

In recent years, in an internal combustion engine such as an automobile, in order to further reduce environmentally hazardous substances such as nitrogen oxides and carbon dioxide contained in combustion exhaust gas, further improvement in fuel consumption and lean combustion are desired. .
As an engine capable of simultaneously improving the combustion efficiency of the engine and reducing the environmental load, it is impossible to propagate the flame with a spark plug using a conventional spark discharge by injecting gas in a high-temperature and high-pressure plasma state into the engine combustion chamber. A method for efficiently burning a lean air-fuel mixture has attracted attention.

As such an igniter, Patent Document 1 discloses a housing that has an opening and a bottom surface facing the opening and that defines a chamber having a circular cross section extending in the axial direction, and is provided on the surface of the housing. An external electrode having an external electrode hole communicating the opening of the chamber and the outside, and a center electrode disposed on the bottom surface of the chamber, and a voltage is applied between the center electrode and the external electrode. An ignition device for an internal combustion period in which a plasma is generated in the chamber by being applied, and a plasma jet is ejected from an opening of the chamber, the volume of the chamber being 10 mm ³ or less, and the axial direction of the chamber An internal combustion engine ignition device is disclosed in which an aspect ratio of a length to an inner diameter is 2 or more.

  According to the ignition device of Patent Document 1, the reach distance when the gas in a high-temperature and high-pressure plasma state is injected in the chamber is increased, and in the lean stratified combustion engine, the fuel concentration in the air-fuel mixture is relatively It was expected that the high part could be reached and the ignitability of the lean fuel engine could be improved.

JP 2006-294257 A

However, in such an igniter, the insulation in the discharge space is broken by the application of a high voltage, and a large current is supplied into the discharge space because it is very short of 10 μsec or less. The time during which the gas in the plasma state can maintain the high energy state is extremely short.
For this reason, in order for flame nuclei to grow and propagate to the air-fuel mixture in the engine combustion chamber to cause ignition, for example, it was necessary to supply a relatively high energy of 200 mJ. In addition, there is a limit to the dilution of the combustible mixture while supplying such high energy.
Further, when such high energy is supplied, the electrodes are consumed very much, which limits the improvement of durability and reliability as an ignition device.
In recent years, in order to improve the mixing of fuel and compressed air, the swirl ratio has been increased, or strong tumble vortices have been generated in the combustion chamber by mixing with a supercharger, etc. In the conventional plasma igniter, flame nuclei injected into the combustion chamber are blown away by a powerful in-cylinder airflow, and energy is generated before growing into flame nuclei large enough for ignition. It may disappear and ignition of the non-ignitable engine may be more difficult.

  Therefore, in view of such circumstances, the present invention injects a gas in a plasma state into a combustion chamber of a non-ignition combustion engine such as a lean homogeneous fuel engine, a lean stratified combustion engine, a supercharged mixed combustion engine or an ammonia combustion engine. It is an object of the present invention to provide an ignition device that ignites an engine and promotes the growth of flame nuclei, has excellent ignitability, and excellent durability.

  According to the first aspect of the present invention, a long-axis center electrode, an insulator formed in a substantially cylindrical shape covering the center electrode and extending below the lower end surface thereof, and covering the insulator, the insulator A discharge space is defined by a ground electrode provided with a ground electrode opening that communicates with the opening, and a high voltage is applied to the discharge space from a discharge power source and a large current is supplied from a plasma energy supply power source. In the ignition device for igniting the engine by making the gas in the discharge space into a high-temperature / high-pressure plasma state and injecting it into the engine combustion chamber, the gas in the high-temperature / high-pressure state ejected from the discharge space As a rotation imparting mechanism for imparting a rotational force from the outer periphery of the air flow to the center of the air flow, the ground electrode opening is communicated with the lower end opening of the insulator to be flush with the first opening, Projecting toward the tip side, the first Providing a second opening having a rotation imparting space defined by a substantially cylindrical peripheral wall surrounding the opening.

According to the first aspect of the present invention, when the gas in a high-temperature and high-pressure plasma state is injected from the first opening, the opening cross-sectional area increases in the rotation imparting space. A large speed difference is generated between the center and the outer periphery, a rotational force inward from the outer periphery is applied, a strong rotational force is generated in the gas in a high energy state, and the donut shape rotates while expanding in the outer diameter direction. It is injected as a vortex ring.
Since the vortex ring rotates and moves in the combustion chamber, the air resistance during movement decreases and the reach distance can be increased.

In addition, the high energy state gas is confined in the vortex ring without being dissipated by the rotation of the vortex ring, and the surrounding air-fuel mixture is taken into the vortex ring by the rotational force, and in the high energy state gas and vortex ring It reacts efficiently and the flame kernel grows rapidly while maintaining the vortex ring shape.
As a result, the growth of flame nuclei is stabilized, and the ignitability is improved even in inflammable engines such as a lean homogeneous fuel engine, a lean stratified combustion engine, and a supercharged mixed combustion engine.

In particular, as in the present invention, when the second opening is provided so as to protrude toward the distal end side of the first opening and surround the first opening, the gas is injected into a plasma state. The airflow flowing in the direction perpendicular to the direction collides with the second opening, changes the flow in an oblique direction with respect to the plasma injection direction, and forms a drawing flow.
At this time, the rotation of the vortex ring is further strengthened by the vortex generated around the second opening, so that the straightness of the vortex ring is enhanced, the energy confinement effect inside the vortex ring is increased, and the flame kernel is stabilized. Therefore, the ignitability is improved.
Therefore, an ignition device with high ignitability can be realized.

  In addition, according to the invention of claim 1, since the energy supplied from the plasma energy supply power source can be held in the flame kernel for a longer time, it can be efficiently used for the growth of the flame kernel, Lower energy can lead to ignition. Therefore, consumption of the electrodes can be suppressed, and a highly reliable ignition device can be realized in terms of durability.

On the other hand, regardless of the present invention, the ground electrode opening is not flush with the lower end opening of the insulator, and the ground electrode opening is exposed so that a part of the lowermost end surface of the insulator is exposed. When a high voltage is applied between the center electrode and the ground electrode, creeping discharge occurs over the surface of the insulator in the discharge space. Since the opening 1 has a large opening, the anisotropy of the creeping discharge is strong, and the gas that is strongly bent in the direction opposite to the side where the creeping discharge occurs and is in a plasma state is injected.
For this reason, when the present invention is not used, since anisotropy appears in the shape of the vortex ring, it becomes difficult to maintain the shape of the vortex ring, the straightness of the vortex ring is weakened, the energy containment effect is weakened, and the flame kernel grows. Is assumed to be unstable.

Further, as in the invention of claim 2, when the height of the peripheral wall surface of the second opening is H ₂ (mm), H ₂ is set in a range satisfying the relationship of the following formula 1. desirable.
0 <H ₂ ≦ 2.7 ... Equation 1

By setting the range of the second opening circumferential wall of the height H ₂ of the second aspect invention, it was found to be longest maintaining the vortex ring.

In the invention of claim 3, the length of the insulating body peripheral wall extending to the inner wall upper edge of the ground electrode opening from the lower end face of the center electrode forming the discharge space and H _1, the inner diameter of the insulating body wall the when the [phi] D _1, and H ₁ and D ₁ is set to a range satisfying the relation of the following formula 2.
H ₁ / D ₁ ≧ 1.5... Formula 2

  According to the invention of claim 3, it is possible to lengthen the reach distance when the gas in the high energy state in the discharge space is ejected in a vortex shape. Therefore, it is possible to realize an ignition device having extremely excellent ignitability. In addition, even if the aspect ratio is set shorter than in the prior art, the reach distance of the gas in a high energy state can be maintained longer, so that the required voltage can be lowered and durability can be expected to be improved.

Further, as in the invention of claim 4, the opening diameter of the _first opening is φD1,
The distance between the opposing wall surfaces of the second opening when the D _2, together with the D ₁ and D ₂ are set to satisfy the relation of the following formula 3, the peripheral wall surface of the second opening (A) a cylindrical shape having an inner diameter φD ₂ equal to the inter-wall distance D ₂ , or (b) the peripheral wall surface of the second opening has a short-axis distance between the wall surfaces D. ₂ is equal to ₂ and the distance between the wall surfaces in the major axis direction is D ₃ a longer than this, or an oval cylinder shape, or (c) the peripheral wall surface of the second opening is in the minor axis direction. wall distance of to a rectangular tubular any shape having a long D _{3 b} than the wall distance of equal longitudinal direction to the wall surface distance D ₂ is this desirable.
1.0 × D ₁ <D ₂ <4.5 × D ₁ Formula 3

  In a fifth aspect of the present invention, supply of a large current from the plasma energy generating power supply is divided into a plurality of times by a pulse current in response to one high voltage application from the discharge power supply.

  According to the invention of claim 5, the gas in the plasma state, which is injected in the vortex ring state and follows the flame nucleus in the middle of the growth, periodically collides, accelerates the peripheral speed of the vortex ring, and takes in higher energy into the vortex ring. Can grow into a larger flame kernel. Therefore, it is possible to realize an ignition device having extremely excellent ignitability.

1 is an overall view showing a configuration of an ignition device according to a first embodiment of the present invention. (A) is the equivalent circuit schematic which shows the outline | summary of the ignition device in the 1st Embodiment of this invention, (b) is the electric current characteristic diagram. (A) is the other equivalent circuit diagram applicable to the ignition device in the 1st Embodiment of this invention, (b) is the electric current characteristic diagram. (A) shows the result of simulating the state after 0.1 ms, and FIG. 4 (b) is a flow analysis diagram showing the result of simulating the state after 0.35 ms. The schematic diagram which shows the mode of the growth of the flame kernel injected from the ignition device of this invention shown in order from (a) to (b). The effect of this invention is shown, (a) is principal part sectional drawing at the time of the plasma injection of the ignition device in the 1st Embodiment of this invention, (b) is the flame kernel in the 1st Embodiment of this invention. The schematic diagram which shows a growth process. (A) is principal part sectional drawing at the time of the plasma injection of the conventional ignition device shown as a comparative example, (b) is a schematic diagram which shows the growth process of the flame kernel in the conventional ignition device. The characteristic view which shows the effect which it has on the combustion fluctuation | variation of this invention with a comparative example. The characteristic view which shows the effect which it has on the lean limit air fuel ratio of this invention with a comparative example. The characteristic view which shows the effect with respect to the ignitability of this invention with a comparative example. The characteristic view which shows the effect with respect to the required energy of this invention with a comparative example. The characteristic view which shows the effect with respect to the durable improvement of this invention, and shows the change of the electrode consumption with respect to input energy. The characteristic view which shows the effect with respect to the wall surface height in the ignition device of this invention with a comparative example. The characteristic view which shows the effect with respect to the aspect-ratio of this invention with a comparative example. The characteristic view which shows the optimal condition of the distance between wall surfaces in the ignition device of this invention with a comparative example. (A) is principal part sectional drawing and its bottom view of the spark plug in the 1st Embodiment of this invention, (b), (c) is a modification of the rotation provision mechanism in the 1st Embodiment of this invention. The principal part sectional drawing which shows this, and its bottom view. (A) is principal part sectional drawing of the ignition plug 10c shown as the comparative example 1, (b) is a flow-analysis figure when 0.35 ms passes, (c) is an enlarged view of A part in this figure (b). Figure. (A) is principal part sectional drawing of the spark plug 10 in the 1st Embodiment of this invention, (b) is a flow analysis figure when 0.35 ms passes, (c) is this figure (b). The enlarged view of A part. (A) is principal part sectional drawing of the spark plug 10d in the comparative example 2 which cannot exhibit the effect of this invention, (b) is principal part sectional drawing which shows the problem in this comparative example 2. FIG.

  An ignition device 1 according to a first embodiment of the present invention will be described with reference to FIG. In this embodiment, the ignition device 1 includes an ignition plug 10, a discharge power source 20 that applies a high voltage to the spark plug 10, and a plasma energy supply power source 30 that supplies a large current. The tip is exposed in the combustion chamber 400 that is mounted on the substantial engine 40.

  The spark plug 10 includes a long-axis center electrode 110, a substantially cylindrical insulator 120 that covers and holds the outer periphery of the center electrode 110, and a substantially cylindrical ground electrode 130 that covers the insulator 120. Yes.

  The center electrode 110 is made of a material having high heat resistance and good electrical conductivity, and a central electrode central shaft 111 made of a material having good electrical conductivity and good heat conductivity is formed on the proximal end side of the center electrode 110, and A central electrode terminal portion 112 connected to the discharge power source 20 and the plasma energy supply power source 30 is formed at the base end.

  The insulator 120 is made of high-purity alumina or the like excellent in heat resistance, mechanical strength, high-temperature dielectric strength, thermal conductivity, and the like, and is formed in a cylindrical shape that extends downward from the tip surface of the center electrode 110. . An insulator locking portion 121 having a large diameter is formed in the middle of the insulator 120, and the inside of the housing portion 13 is interposed via a seal member (not shown) that maintains airtightness with the housing portion 13 described later. It is locked to. On the base end side of the insulator 120, a corrugated insulator head 123 is formed that insulates the center electrode terminal portion 112 and the surface of the housing portion 13 and prevents high-voltage leakage.

The ground electrode 130 is made of a conductive metal material, is formed in a substantially cylindrical shape so as to cover the insulator 120, bends toward the center on the tip side, covers the bottom of the insulator 120, and opens at the lower end of the insulator 120. A first opening 131 communicating with the same surface is formed.
A discharge space 140 is defined by the inner peripheral wall of the insulator 120, the bottom surface of the center electrode 110, and the first opening 131.

  The ground electrode 130 has a cylindrical peripheral wall surface 133 projecting toward the distal end side of the first contact opening 131 so as to surround the first opening 131 as a rotation imparting mechanism that is a main part of the present invention. A second opening 132 having a partitioned rotation imparting space 141 is formed.

In the present embodiment, the distance from the lower end surface of the center electrode 110 exposed to the discharge space 140 to the boundary between the inner peripheral wall of the first opening 131 and the insulator 120, in other words, the center forming the discharge space 140. the length of the insulating body wall extending from the lower end surface of the electrode 110 on the inner wall upper edge of the ground electrode opening 131, i.e., the length H ₁ of the discharge space 140, the height of the peripheral wall surface 133 of the second opening 132 and H _2, the inner diameter of the inner peripheral wall of the insulator 120, i.e., the inner diameter [phi] D ₁ of the first ground electrode 131 that communicates with the inner diameter flush of the discharge space 140, the inner diameter [phi] D ₂ of the second opening 132 The relationship is set to H ₁ = 3.0 mm, H ₂ = 1.0 mm, φD ₁ = 1.3 mm, and φD ₂ = 3.0 mm so as to satisfy the relationships of the following formula 1, formula 2, and formula 3. .
0 <H ₂ ≦ 2.7 ... Equation 1
H ₁ / D ₁ ≧ 1.5... Formula 2
1.0 × D ₁ <D ₂ <4.5 × D ₁ Formula 3

The outer peripheral portion of the ground electrode 130 extends in a cylindrical shape toward the proximal end so as to cover the outer periphery of the insulator 120, and a back electrode portion 134 that is opposed to the center electrode 110 through the insulator 120 is extended. .
Further, the base end side of the back electrode 134 is fixed to the engine combustion chamber wall surface 40 (not shown) so that the second opening 132 is exposed in the engine combustion chamber 400 (not shown) while holding the insulator 120. In addition, a housing portion 13 is formed for electrically grounding the ground electrode 130 and the combustion chamber wall surface 40. A screw part 135 for screwing to the combustion chamber wall surface is formed on the outer periphery of the back electrode part 134, and a hexagonal part 136 for tightening the screw part 135 is formed on the outer peripheral part on the proximal end side of the housing part 13. Further, a caulking portion 137 is formed for caulking and fixing the insulator 120 in the housing portion 13.

  FIG. 2A shows an equivalent circuit of the ignition device 1 of the present invention. The discharge power source 20 includes a first power source 21, an ignition key 22, an ignition coil 23, an ignition coil drive circuit 24, an electronic control device 25, a first rectifier element 26, and a radio noise absorbing resistor 27. . The discharge power source 20 is desirably rectified by the first rectifying element 26 so that the center electrode 110 becomes an anode in order to suppress electrode consumption.

  The power source 30 for generating plasma energy includes a second power source 31, a radio noise absorbing resistor 32, a second rectifier element 34, and a plasma energy charging capacitor 33. In order to suppress electrode consumption, the plasma energy generating power supply 30 is desirably rectified by the second rectifying element 34 so that the center electrode 110 becomes an anode.

When a high voltage is applied from the discharge power supply 20 and a breakdown discharge that breaks the insulation in the discharge space 140 occurs, the energy stored in the plasma energy charging capacitor 33 becomes a large current IP and an extremely short discharge time TP. It is released at a stretch. In FIG. 2 (b), at this time, illustrating the relationship between the energy to be introduced and the discharge current IP and the discharge time T _P.

  Further, as shown in FIG. 3A, by providing a plurality of choke coils 35 and capacitors 33 in parallel with the plasma energy charging capacitor 33, as shown in FIG. In this case, the same amount of energy as that emitted in the above can be divided into two or more peaks and supplied. The choke coil 35 has a low inductance on the downstream side and a high inductance on the upstream side. The breakdown in the discharge space 140 is broken by the breakdown discharge from the discharge power source 20, and first, a first stage of large current is discharged from the capacitor 33 in which the choke coil 35 is not interposed. The second-stage current is released from the capacitor 33 delayed by the choke coil 35, and further, the third-stage current is released from the capacitor 33 delayed by the high-inductance choke coil 35.

The effect of the present invention in this embodiment will be described with reference to FIGS.
FIG. 4 is an analysis diagram of a jet flow when high-temperature and high-pressure plasma is injected from the spark plug 10 according to the present embodiment. FIG. 4A shows a result of simulating a state after 0.1 ms, FIG. 4B shows the result of simulating a state after 0.35 ms.
FIG. 5 is a schematic diagram showing the growth of flame nuclei injected from the ignition device of the present invention shown in order from (a) to (b).
FIG. 6 (a) is a cross-sectional view of the main part schematically showing the state of the spark plug 10 during discharge in the present embodiment, and FIG. 6 (b) is an internal combustion engine using the ignition device 1 of the present invention. It is a schematic diagram which shows the growth process of the flame kernel in a combustion chamber.
As a comparative example, FIG. 7 shows a case where a conventional spark plug 10z is used. FIG. 7A is a main part sectional view schematically showing a state of the conventional spark plug 10z during discharge, and FIG. 7B is a schematic diagram showing a growth process of flame nuclei.

  When a high voltage is applied from the discharge power supply 20, the insulation between the lower end surface of the center electrode 110 and the ground electrode opening 131 is broken, and the breakdown discharge BDW is caused to crawl the inner peripheral wall surface of the insulator 120. Occur. At this time, a large current flows from the plasma energy supply power source 30, high energy electrons are discharged around the discharge path in the discharge space 140, the gas in the discharge space 140 is ionized, and a high temperature / high pressure plasma state is obtained. Then, it is ejected from the discharge space.

At this time, as shown in FIGS. 4A and 6A, the plasma-state gas PZ ejected from the discharge space 140 moves in the outer diameter direction in the rotational force applying space 141 provided as the rotation applying mechanism. Because of the expansion, the difference between the velocity at the central portion of the plasma state gas PZ ejected from the discharge space 140 and the velocity near the inner peripheral wall surface 133 of the second opening portion 132 becomes large, and the gas in the plasma state A vortex is generated from the inside toward the outside.
As shown in FIG. 4B, a rotational force is applied to the plasma state gas PZ by this vortex, and this rotational force is maintained even after being ejected from the rotational force applying space 141, and a vortex field is formed inside. As shown in FIG. 6B, a donut-shaped vortex ring that advances in the injection direction while rotating while expanding in the outer diameter direction is formed.
Since the vortex ring moves in the combustion chamber 400 while rotating, the air resistance at the time of movement decreases and the reach distance can be increased, so that the flame kernel can reach a desired position of the air-fuel mixture.
In addition, as shown in FIG. 5 (a), the high-energy gas PZ is confined inside the vortex ring, and the surrounding air-fuel mixture is taken into the interior by rotation, and the mixture is given high energy confined in the vortex ring. It is done.

Further, even if an air flow is generated in the cylinder, the straightness is increased by the strong rotational force of the vortex ring. For this reason, even immediately after being injected from the spark plug 10 in which sufficient flame nuclei are not grown, the flame nuclei can reach a desired position in the combustion chamber without being caused to flow by the in-cylinder airflow.
Further, as shown in FIGS. 5B and 6B, the flame kernel grows greatly while maintaining the donut shape while taking in the surrounding air-fuel mixture by the rotational force of the ring.
As a result, the growth of the flame kernel is stabilized, and the ignitability is improved even in a hardly ignitable lean combustion engine. Therefore, an ignition device with high ignitability can be realized.
In addition, the energy supplied from the plasma energy supply power source 30 can be held inside the flame kernel for a longer time due to the confinement effect of the vortex ring. Therefore, it can be efficiently used for the growth of flame nuclei and lead to ignition with lower energy.

  As shown in FIG. 6B, in-cylinder airflow such as tumble vortex and swirl is generated in the engine combustion chamber 400, and the vortex ring-shaped flame kernel injected from the spark plug 10 is immediately after injection. Because of the strong rotational force and straightness, it grows while taking in the surrounding air-fuel mixture inside without being swept away by the in-cylinder airflow, and goes straight in the combustion chamber 400 to grow into a relatively large and stable flame kernel. In a state in which the moving speed is reduced to some extent, the mixture in the combustion chamber 400 moves along the in-cylinder airflow while taking the air-fuel mixture in the combustion chamber 400 into the vortex ring, and grows into a larger flame nucleus. It is possible to ignite a combustion engine or a supercharged mixed combustion engine.

On the other hand, in the conventional spark plug 10z, as shown in FIG. 7A, the plasma-state gas PZ ejected from the discharge space 140z generates a tear-granular flame nucleus having a relatively large volume.
As shown in FIG. 7 (b), flame nuclei injected into the combustion chamber 400 from the conventional spark plug 10z move along the in-cylinder airflow and react with the surrounding air-fuel mixture to grow into flame nuclei. To do.
However, in the conventional spark plug 10z, since the opening diameter of the ground electrode opening 131z is small, the eddy current generated in the flame kernel is small, lacks straightness, and grows into a flame kernel large enough for ignition. It is easy to flow by the in-cylinder airflow, and the power to confine the high energy gas in the flame kernel inside the flame kernel is also small, so the energy inside the flame kernel diffuses easily and the flame nucleus is sufficient to ignite the ignition system There is a risk that it will not grow to a large size.

8 to 15 show test results representing the effects of the present invention together with comparative examples.
Test results using the conventional spark plug 10z shown in FIG. 7 are shown as comparative examples, and test results using the spark plug 10 according to the first embodiment of the present invention are shown as examples. Furthermore, a test result using the circuit shown in FIG. 2 is shown as Example 1, and a test result using the circuit shown in FIG.
In this test, an ignition plug is mounted on a cylinder simulating an engine, and fuel and air are introduced at a predetermined air-fuel ratio and ignited under the same conditions. Measured cycle combustion pressure waveform and calculated the variation of the indicated mean effective pressure (COV IMEP), (2) Combustion stable lean limit air-fuel ratio read with COV IMPEP 5% as criteria, (3) Initial combustion Period and main combustion period, (4) A comparative test was conducted on the energy reduction effect at a predetermined air-fuel ratio.

  As shown in FIG. 8, at any air-fuel ratio, the combustion fluctuation (COV IMEP) of the example of the present invention is smaller than that of the comparative example, and according to the ignition device of the present invention, stable ignition can be obtained. There was found.

  Further, as shown in FIG. 9, the lean limit air-fuel ratio that can be stably combusted for the same input energy (200 mJ) at a predetermined in-cylinder pressure (0.2 MPa) is shown in Comparative Example (23.8). Compared to the embodiment (25.3) of the present invention, it was found that the ignition device of the present invention can be ignited even at a leaner air-fuel ratio.

Further, as shown in FIG. 10, initial combustion defined by a crank angle from ignition to a combustion rate of 10% and main combustion defined by a crank angle from a combustion rate of 10% to a combustion rate of 90%. According to the present invention, it has been found that the combustion period can be significantly shortened compared to the conventional case, and the ignition device of the present invention exhibits excellent ignitability.
Further, in the present invention, the energy supplied to the spark plug 10 for one ignition is more than once when energy is supplied to the spark plug 10 for one ignition at a time (Example 1). It was confirmed that a more stable combustion can be obtained with the separately supplied one (Example 2).

FIG. 11 shows the effect of reducing the required energy of the present invention. As a comparative example, the first spark plug 10z is used, and at the same air-fuel ratio as the air-fuel ratio at which stable ignition is possible with the energy of 200 mJ, the first The result using the spark plug 10 shown in the embodiment is shown.
As shown in FIG. 11, according to the present invention, it has been found that the energy required for stable ignition at the same air-fuel ratio as in the comparative example can be reduced by about 60% compared to the comparative example.

FIG. 12 is a characteristic diagram showing the effect on durability of the present invention and showing changes in the amount of electrode consumption with respect to each supply energy.
As described above, according to the present invention, since the required energy required for ignition can be reduced, as shown in FIG. 12, it is possible to suppress the consumption of the electrode by reducing the input energy, The reliability as an ignition device can be further improved.

Referring to FIG. 13, described the height effects of _{H 2} peripheral wall surface 133 of the second opening 132.
FIG. 13 shows, as a comparative example, the combustion fluctuation when the conventional spark plug 10z is used, and shows the measurement result of the combustion fluctuation when H ₂ of the spark plug 10 shown in the first embodiment of the present invention is changed. FIG.
As shown in FIG. 13, it has been found that when the H ₂ is in the range of the following formula 1, the combustion fluctuation is smaller when the spark plug 10 of the present invention is used than when the comparative example is used.
0 <H ₂ ≦ 2.7 ... Equation 1
Further, it has been found that it is more preferable to set H ₂ in the range of 0.5 ≦ H ₂ ≦ 2.3. If H ₂ is set within this range, a more stable ignitability with a COV IMEP of 5% or less can be obtained.
When H ₂ is set to be larger than 2.7 mm, the combustion fluctuation becomes larger than that in the past, but this is more effective than the effect of generating a vortex ring by applying rotation to the flame extinguishing effect by diffusion of thermal energy to the peripheral wall surface 133. This is thought to be because it grows.

With reference to FIG. 14, the effect of reducing the aspect ratio H ₁ / D ₁ between the inner diameter φD _{1 of} the first opening 131 and the length H ₁ of the discharge space 140 will be described.
Conventionally, it is desirable to increase the aspect ratio H ₁ / D ₁ as much as possible in order to lengthen the ejection distance of the gas in a plasma state, for example, H ₁ / D ₁ > 2 is good. .
However, when the aspect ratio H ₁ / D ₁ is increased, the required voltage required to break the insulation in the discharge space 140 increases, and the electrode may be consumed quickly.
Therefore, as a comparative example, the aspect ratio H ₁ / D ₁ of the conventional spark plug 10z is set to 2, and the aspect ratio of the spark plug 10 in the first embodiment of the present invention is changed variously. The aspect ratio H ₁ / D ₁ at which stable combustion fluctuations can be obtained even with the equivalent lean limit A / F (25.3) was investigated.
As a result, as shown in FIG. 14, according to the present invention, it has been found that even if H ₁ / D ₁ is 1.5, the same combustion fluctuation as in the comparative example can be obtained, and the inner diameter of the first opening 131 is obtained. obtained by setting the aspect ratio H _{1 /} D ₁ between the length H ₁ of the [phi] D ₁ and the discharge space 140 in a range satisfying the following equation 2, the finding that the resulting stable ignitability while suppressing consumption of the electrodes It was.
H ₁ / D ₁ ≧ 1.5... Formula 2

Referring to FIG. 15, a description will be given of an effect of the wall distance D ₂ opposite the second opening 132.
Figure 15 is a combustion variation when a conventional spark plug 10z as Comparative Example, the measurement result of combustion variation in the case of changing the D ₂ of the spark plug 10 shown in the first embodiment of the present invention FIG.
As shown in FIG. 15, D ₂ is in the range of the following formula 3, combustion variation than the comparative examples preferable to use a spark plug 10 of the present invention that the decrease was found.
1.0 × D ₁ <D ₂ <4.5 × D ₁ Formula 3
Further, it has been found that it is better to set D _{2 in} a range of 1.15 × D ₁ ≦ D ₂ ≦ 4.25 × D ₁ . If D ₂ is set within this range, a more stable ignitability with a COV IMEP of 5% or less can be obtained.

FIGS. 16A to 16C show spark plugs 10, 10 a, and 10 b as modifications of the spark plug in the first embodiment of the present invention.
In the drawing, the left side shows a cross-sectional view of the main part, and the right side shows a bottom view thereof.
As shown in FIG. 5A, the peripheral wall surface 133 of the second opening 132 may be formed in a cylindrical shape having an inner diameter φD ₂ equal to the inter-wall distance D ₂ , or as shown in FIG. the second opening of the peripheral wall 133a, equal to the wall surface distance between the wall surface distance D ₂ along the short axis, the long axis direction of the wall surface distance between the elliptic cylindrical shape having a long D _{3 a} than this, or may be formed into oval tubular, as shown in (c), the peripheral wall 133b of the second opening 132b, the wall distance of the minor axis is equal to the wall distance D _2, the length wall distance in the axial direction may be formed in rectangular tubular shape having a long D _{3 b} than this.
In the present embodiment, the effect of the present invention can be obtained if at least the inter-wall distance D ₂ is set so as to satisfy the relationship shown in the above expression 3, and the inter-wall distances D ₃ a, D in the major axis direction can be obtained. ₃ b can be changed as appropriate to change the spreading direction of the flame kernel in accordance with the combustion characteristics of the internal combustion engine to be applied.

With reference to FIG. 17, FIG. 18, the desirable form of the rotational force provision mechanism which is the principal part of this invention is explained in full detail.
FIG. 17A shows a comparative example 1 in which a ground electrode 130c is formed thick and a peripheral wall surface 133c is formed by expanding a part of the front end side of the first opening 131c in the outer diameter direction. FIG. 17B is a cross-sectional view of the main part of the spark plug 10c that divides the rotational force applying space 141c by forming the opening 132c of FIG. 2, and FIG. 17B is a diagram in which high energy is applied to the plasma spark plug 10c in Comparative Example 1. FIG. 17C is a flow analysis diagram showing a simulation result of the plasma jet when 0.35 ms has elapsed after that, and FIG. 17C is an enlarged view of a portion A in FIG.

  On the other hand, FIG. 18A shows a cylindrical shape that protrudes toward the distal end side of the first opening 131 so as to surround the first opening 131, which is shown as the first embodiment of the present invention. FIG. 18B is a cross-sectional view of the main part of the spark plug 10 in which the second opening 132 having the rotation imparting space 141 partitioned by the peripheral wall surface 133 is formed, and FIG. 18B is a plan view of the plasma spark plug 10 in the present embodiment. FIG. 18C is a flow analysis diagram showing a simulation result of a plasma jet when 0.35 ms elapses after energy is applied, and FIG. 18C is an enlarged view of a portion A in FIG.

Also in Comparative Example 1, as shown in FIG. 17 (b), vortex flow is generated in the rotational force applying space 141c, and even after jetting from the rotational force applying space 141c, the vortex field as shown in FIG. 17 (c). Is formed.
Also in this comparative example, the ignitability was improved as compared with the conventional plasma ignition device due to the generation of the vortex ring as in the above embodiment, but the first opening so as to surround the first opening 131. It has been found that the rotational force of the vortex ring is weak and the ignitability is inferior to the above embodiment in which the second openings 132, 132a, 132b are provided in a cylindrical shape on the tip side of the portion 131 and protrude into the combustion chamber.
This is because, as shown in FIG. 17C, in Comparative Example 1, the flow in the direction perpendicular to the injection direction is strong on the surface of the second opening 132c, and the injection speed is suppressed. Inferred.

  On the other hand, in the first embodiment of the present invention, as shown in FIGS. 18B and 18C, an air flow perpendicular to the injection direction is generated in the second opening 132 protruding into the combustion chamber. Colliding and changing the flow in an oblique direction with respect to the injection direction to form a drawing flow, the vortex generated around the second opening 132 further strengthens the rotation of the vortex ring. It is presumed that the effect of confining energy inside the vortex ring increases, the flame kernel grows stably, and the ignitability improves.

Below, with reference to FIG. 19, the comparative example 2 which cannot exhibit the effect of this invention is demonstrated.
As Comparative Example 2, as shown in FIG. 19A, the opening diameter of the ground electrode opening 131d is larger than the opening diameter of the insulator 120 forming the discharge space 140, and the rotation imparting space 141d is formed. It is also possible.
However, in this comparative example, the ignitability was improved as compared with the conventional plasma ignition device due to the generation of the vortex ring as in the above embodiment, but the second openings 132, 132a, 132b were formed in the cylinder. It has been found that the rotational force of the vortex ring is weak and the ignitability is inferior compared to the first embodiment described above, which is provided in a shape and protrudes into the combustion chamber.

In Comparative Example 2, a part of the lowermost end surface of the insulator 120 is exposed, and when a high voltage is applied between the center electrode 110 and the ground electrode 130, the insulator 120 is insulated in the discharge space 140. Creeping discharge occurs over the surface of the body 120, but since the first opening 131d of the ground electrode 130d is large, the anisotropy of creeping discharge is strong, as shown in FIG. Then, a gas that is strongly bent in a direction facing the side where the creeping discharge is generated and is in a plasma state is injected. For this reason, since anisotropy appears in the shape of the vortex ring, it is difficult to maintain the shape of the vortex ring, the rectilinearity of the vortex ring is weakened, the energy containment effect is weakened, and it is assumed that the growth of the flame kernel becomes unstable. .

In addition, unless it deviates from the meaning of this invention, according to the magnitude | size of the engine to apply, the kind of fuel, and the driving | running condition of an engine, the specific shape of a rotation provision mechanism can be changed suitably. For example, in the above-described embodiment, the plasma ignition device constituted by a single spark plug has been described. However, the present invention can also be applied to a multi-cylinder engine including a large number of spark plugs.
Further, in the above embodiment, the case where the high voltage power source is constituted by the two power sources of the discharge power source 20 and the plasma energy generating power source 30 has been described. And may be applied as a discharge power source and a plasma energy generation power source. Further, in the above-described embodiment, the case where a normal ignition coil is used as the boosting circuit of the discharge power supply has been described as an example. However, a capacitor discharge ignition coil (C.D.I.), a piezoelectric transformer or the like is used. May be.

DESCRIPTION OF SYMBOLS 1 Ignition device 10 Spark plug 110 Center electrode 120 Insulator 130 Ground electrode 131 1st opening part 132 2nd opening part 133 Circumferential wall surface 140 Discharge space 141 Rotation imparting space φD ₁ Discharge space inner diameter (insulator inner peripheral wall inner diameter)
D ₂ Distance between wall surfaces of second opening H ₁ Discharge space length H ₂ Second opening length (rotation imparting space length)
20 Power supply for discharge 30 Power supply for plasma energy supply 40 Internal combustion engine 400 Engine combustion chamber

Claims (5)

A long-axis center electrode, an insulator formed in a substantially cylindrical shape that covers the center electrode and extends below the lower end surface thereof, and a ground that covers the insulator and communicates with the opening of the insulator A discharge space is defined by a ground electrode provided with an electrode opening, and a high voltage is applied from the discharge power source and a large current is supplied from the plasma energy supply power source to the discharge space. In an ignition device that ignites the engine by injecting the gas inside into a high-temperature, high-pressure plasma state and injecting the gas into the engine combustion chamber,
As a rotation imparting mechanism that imparts a rotational force from the outer periphery of the air flow toward the center of the gas flow in a high temperature / high pressure state ejected from the discharge space,
The ground electrode opening is communicated flush with the lower end opening of the insulator to form a first opening, which protrudes toward the distal end side of the first opening and is formed by a substantially cylindrical peripheral wall surface surrounding the first opening. An ignition device comprising a second opening having a partitioned rotation imparting space. 2. The ignition device according to claim 1, wherein when the height of the peripheral wall surface of the second opening is H ₂ (mm), H ₂ is set to a range that satisfies the relationship of the following expression 1.
0 <H ₂ ≦ 2.7 ... Equation 1 The length of the insulating body wall extending to the inner wall upper edge of the ground electrode opening from the lower end face of the center electrode forming the discharge space and H _1, the inner diameter of the insulating body wall when a [phi] D ₁ The ignition device according to claim ₁ , wherein H ₁ and D ₁ are set in a range satisfying a relationship of the following formula 2.
H ₁ / D ₁ ≧ 1.5... Formula 2 When the opening diameter of the _first opening is φD ₁ and the distance between the opposing wall surfaces of the second opening is D ₂ , the range in which D ₁ and D ₂ satisfy the relationship of the following expression 3 And set
The peripheral wall surface of the second opening is
(A) a cylindrical shape having an inner diameter φD ₂ equal to the inter-wall distance D ₂ , or
(B) The elliptical cylinder in which the peripheral wall surface of the second opening has D ₃ a in which the distance between the wall surfaces in the short axis direction is equal to the distance D ₂ between the wall surfaces and the wall surface distance in the long axis direction is longer than this. Or oval cylinder or
(C) The peripheral wall surface of the second opening has a rectangular cylindrical shape in which the distance between the wall surfaces in the short axis direction is equal to the distance D ₂ between the wall surfaces and the distance between the wall surfaces in the long axis direction is longer than D ₃ b. The ignition device according to any one of claims 1 to 3, wherein the ignition device has any one of the shapes.
1.0 × D ₁ <D ₂ <4.5 × D ₁ Formula 3   5. The supply of a large current from the plasma energy generation power source is divided into a plurality of times by a pulse current and supplied with a high voltage from the discharge power source once. Ignition device according to.

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