JP2010053835A - Liquid injection device and liquid fuel injection arrangement - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To attain a liquid injection device flying liquid over a long distance in large quantity and in minute particle sizes. <P>SOLUTION: The liquid injection device 100 for injecting liquid from a nozzle 12 has a compression chamber 14 which communicates with the nozzle 12 and has a drive unit 16 pressurizing the liquid in the chamber. Representing a pulsation cycle of pressure applied to the interior liquid in the compression chamber 14 by the drive unit 16 as Tp, the speed of the pressure pulsation as V and the moving distance of the pulsation according to a distance from the drive unit 16 to the nozzle 12 as L, the pulsation cycle Tp is equal to 2L/V. The drive unit 16 pressurizes the interior liquid at pressurization starting timing Ts satisfying 0.5Tp<Ts≤Tp, positively causes disturbance in the pulsation and injects the liquid from the nozzle 12. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a liquid ejecting apparatus and a fuel ejecting apparatus in which the ejected liquid droplets are less combined.

  A technique for ejecting liquid is well known as an inkjet technique in printer applications. For example, in Patent Document 1, in an ink jet printer (recording apparatus), ink droplets ejected from nozzles are merged in a path to the paper surface, and the volume variation of the ink droplets ejected is corrected according to the number of coalescings. Is described.

  Patent Document 2 describes that, in an inkjet head for a printer, bubbles are ruptured in the vicinity of a nozzle opening to form a fine droplet and adhere to a storage object.

  Patent Document 3 describes that an ink mist is ejected using ultrasonic vibration in an ink jet head for a printer. Note that Patent Document 3 proposes increasing the degree of nozzle integration by making the wall surface shape of the ink liquid chamber as viewed from the nozzle direction a rectangle or an ellipse.

JP 2002-211011 A JP-A-1-306258 JP 2002-225260 A

  It is desired that various liquid fuels used as fuel in internal combustion engines (engines) typified by vehicles and the like are injected with a uniform and fine particle size and supplied into the engine cylinder. As a technique for ejecting ink, an ink jet technique used in a printer application is well known, but there has been no proposal in the past to apply such an ink jet technique to a mechanism of a fuel ejecting apparatus.

  In addition, when the inkjet technology is applied to a fuel injection device (injector), a larger discharge flow rate and a larger penetration force (long flight distance of discharged droplets) are required as compared with a printing operation. For this reason, if an inkjet technique is adopted, a large amount of liquid droplets must be ejected from the nozzles in a short time. However, such a large amount of liquid ejected in a short period of time tends to cause the union of droplets ejected during flight, and increases the particle size of the droplets.

  Further, in the conventionally known printing application, high-precision positioning is required during the operation, and the ejected droplets are required to fly at the same speed and path every time. Therefore, in the printer application, the pressure driving unit controls the liquid in the flow path from the pressurizing chamber of the print head to the nozzle so as to minimize the disturbance. However, when ink jet technology with such pressure control is applied to a fuel injection device, droplets ejected in the same direction from the nozzles will coalesce while flying over a long distance that is not expected in printing technology. This tends to increase the particle size of the downstream droplet.

  The present invention prevents coalescence of liquids ejected from nozzles, and ejects a large number of fine droplets.

  The present invention is a liquid ejecting apparatus that ejects liquid from a nozzle, and includes a pressurizing chamber that communicates with the nozzle and has a drive unit that pressurizes liquid in a room, and the interior of the pressurization chamber is driven by the drive unit. When the pulsation period of the pressure applied to the liquid is represented by Tp, the speed of the pulsation of the pressure is represented by V, and the movement distance of the pulsation according to the distance from the driving unit to the nozzle is represented by L, the pulsation period Tp is 2 L / V. Equally, the drive unit pressurizes the indoor liquid at a pressurization start timing Ts that satisfies 0.5Tp <Ts ≦ Tp, and ejects the liquid from the nozzle.

  In another aspect of the present invention, the liquid is a liquid fuel for an internal combustion engine, and the liquid fuel injected from the nozzle is supplied to the cylinder.

  In another aspect of the present invention, there is provided a liquid fuel injection device for injecting liquid fuel from a nozzle and supplying the liquid fuel to a cylinder, wherein the drive unit communicates with the nozzle and pressurizes the liquid fuel in the room. The pressurizing chamber is provided, and the driving unit pressurizes the indoor liquid fuel at a timing at which the pulsation of the pressure generated in the indoor liquid fuel in the pressurizing chamber is disturbed, and injects the liquid fuel from the nozzle.

  In another aspect of the present invention, there is provided a liquid fuel injection device for injecting liquid fuel from a plurality of nozzles and supplying the liquid fuel to a cylinder, the liquid fuel injection device being common to the plurality of nozzles, A common liquid chamber for storing liquid, a pressurization chamber having a drive unit for pressurizing liquid fuel in the chamber, communicating with a corresponding nozzle of the plurality of nozzles, and a pressurization chamber corresponding to the common liquid chamber A fluid resistance path for supplying a required amount of liquid fuel from the common liquid chamber to the pressurizing chamber, and the drive unit pulsates the pressure generated in the indoor liquid fuel of the pressurizing chamber. The indoor liquid fuel is pressurized at a disturbing timing, and the liquid fuel is injected from the corresponding nozzle.

  In another aspect of the present invention, in the liquid fuel injection device, the pulsation cycle of the pressure applied to the liquid in the pressurizing chamber by the drive unit is Tp, the pressure pulsation speed V, and the drive unit to the nozzle. When the movement distance of pulsation according to the distance is represented by L, the pulsation cycle Tp is equal to 2 L / V, and the drive unit performs the indoor liquid fuel at the pressurization start timing Ts that satisfies 0.5Tp <Ts ≦ Tp. The liquid fuel is injected from the corresponding nozzle.

  In the present invention, the driving unit that pressurizes the internal liquid pressurizes at a timing that disturbs the pulsation cycle Tp of the pressure applied to the liquid in the pressurizing chamber. Specifically, pressurization is performed at a pressurization start timing Ts that satisfies 0.5Tp <Ts ≦ Tp. By controlling the pressurization timing, a velocity wave other than the traveling direction is generated in the pressure wave from the pressurization chamber to the nozzle, and the liquid ejected from the nozzle is imparted with turbulence utilizing pressure pulsation or turbulence. Can be amplified. Therefore, the droplets ejected from the nozzles are not unevenly distributed, are evenly scattered in the ejection space, and even if the ejected droplets fly over a long distance, the droplets are unlikely to coalesce and have a small particle size. Can be maintained.

  In addition, according to the present invention, a large amount of droplets having a small particle diameter can be sprayed and used as a fuel injection device or the like. In addition, since it is possible to spray droplets with a small particle size, it is possible to prevent fuel loss and combustion failure due to droplets adhering to the wall surface of the intake pipe where fuel is injected. It is advantageous for improvement.

  In addition, since a pressure can be applied by a drive unit in a pressurizing chamber communicating with a nozzle, a pressurizing pump that pumps liquid fuel from a fuel tank and pressurizes and supplies it to a conventional fuel injection valve becomes unnecessary. This is advantageous in reducing the weight and size of the engine system.

  Furthermore, since a plurality of nozzles can be arranged in parallel, the liquid ejecting apparatus can be reduced in weight and thickness.

  Hereinafter, embodiments of the present invention (hereinafter referred to as embodiments) will be described with reference to the drawings. FIG. 1 shows a schematic cross-sectional configuration of a liquid ejecting apparatus according to this embodiment.

  The liquid ejecting apparatus 100 according to the present embodiment includes a nozzle 12, a pressurizing chamber 14, a driving unit 16, and a liquid chamber 20, and a single ejecting apparatus 100 includes a plurality of nozzles 12 arranged in parallel. Each nozzle 12 is connected to a pressurizing chamber 14 provided correspondingly. Each pressurizing chamber 14 has a drive unit 16 for pressurizing indoor liquid as will be described later, and each pressurizing chamber 14 is provided with a plurality of pressurizing units via fluid resistance units 18 provided correspondingly. It is provided in common with the chamber 14 and communicates with a liquid chamber 20 filled with liquid. Note that the fluid resistance unit 18 uses the viscosity, surface tension, and volume of the pressurizing chamber 14 (to the pressurizing chamber) so that the liquid is supplied from the common liquid chamber 20 to the pressurizing chamber 14 without excess or deficiency. The diameter and length are set according to the amount of liquid to be supplied. Further, the volume of the pressurizing chamber 14 and the diameter of the nozzle 12 are also set according to the required injection amount per time, the surface tension (viscosity) of the liquid to be employed, and the like.

  For example, in the case of adopting a liquid having a low viscosity and surface tension, unlike the ink materials employed in so-called conventional inkjet printer applications such as gasoline containing gasoline, kerosene, alcohol, and water, the fluid resistance unit 18 and the nozzle 12 The diameter needs to be smaller than that of the ink material.

  The pressurizing chamber 14 is provided with a drive unit 16 for pressurizing the liquid filling the chamber. The drive unit 16 is not particularly limited as long as the liquid can be discharged from the nozzle 12, but a piezo element, a heating element, or the like can be adopted as an example. When a piezoelectric element is used, the element is deformed by applying a voltage to the element, and the indoor liquid is pressurized using this deformation. When the heat generating element is used, current is supplied to cause the element to generate heat, and bubbles are generated in the vicinity of the element in the pressurizing chamber, thereby pressurizing the indoor liquid.

In the present embodiment, the pressurization by the driving unit 16 is performed at a timing that causes disturbance in the indoor liquid as follows. Specifically, when the application start timing (pressurization start timing) of the pressure applied to the indoor liquid in the pressurizing chamber 14 by the drive unit 16 is Ts and the pulsation cycle of the indoor liquid is Tp, the following equation (1)
0.5Tp <Ts ≦ Tp (1)
The indoor liquid is pressurized so as to satisfy the conditions shown in FIG. The pulsation cycle Tp in the above equation satisfies Tp = 2L / V, where V represents the velocity of pulsation (pressure wave) and L represents the movement distance of pulsation according to the distance from the drive unit 16 to the nozzle 12.

  FIG. 2 shows the relationship between the waveform of the indoor fluid pressure at the drive unit 16 and the pressurization timing at the drive unit 16. When pressure (positive pressure) is applied to the indoor liquid by the drive unit 16 provided at the innermost position (the farthest position) of the pressurizing chamber 14 with respect to the nozzle 12, the indoor fluid pressure in the drive unit 16 increases and is generated. The pulsation (pressure wave) transmitted through the internal liquid of the pressurizing chamber 14 changes the indoor fluid pressure in the drive unit 16 as shown in FIG. The pressure wave that has traveled through the pressurizing chamber 14 in the nozzle direction is reflected by the pressurizing chamber wall surface in the region connected to the nozzle 12 of the pressurizing chamber 14 and returns to the driving unit 16. For this reason, the indoor fluid pressure in the drive unit 16 pulsates at the cycle of (2L / V) as shown in FIG.

  When the driving unit 16 generates pressure pulsation using the piezoelectric effect of the piezo element, in this embodiment, as shown in FIG. 2B, the voltage pulsation is applied to the driving unit during the voltage application period to the piezo element. Return to the period when the hydraulic pressure becomes positive again (see FIG. 2A). The period T in which the liquid is pressurized by the driving unit 16 is synchronized with the pressure pulsation period Tp in which the pressure pulsation in the flow path from the pressurizing chamber 14 to the nozzle 12 returns to the driving unit 16 that pressurizes the liquid (T≈Tp ) And the pressurization start timing Ts is controlled to satisfy the above formula (1). By controlling the voltage application timing to the piezo element in this way, it is possible to increase the disturbance to the pressure pulsation bounced off from the nozzle 12. For this reason, pressure waves generate speeds other than the liquid flow path direction (the direction toward the nozzle 12), and at the nozzle outlet, droplets are not ejected in only one direction, but fly over a long distance. Are scattered in the jetting space as small droplets without merging. In addition, by sequentially pressurizing the internal liquid at the pressurization start timing Ts satisfying the above formula (1) so that the period T is substantially synchronized with the pressure pulsation period Tp, the nozzle 12 can be efficiently and continuously pressurized. The liquid can be discharged on the surface.

  3 and 4 are images of the state of the liquid droplets ejected from the nozzles when the pressurization timing in the pressurization chamber 14 is controlled as in the present embodiment. FIG. 3 shows the state of a droplet near the nozzle outlet, and FIG. 4 shows the state of a droplet 20 mm downstream from the nozzle. The droplet velocity at the nozzle outlet is 12.10 m / s.

  The pressurization timing is controlled so as to satisfy the relationship of the above formula (1), and in this example, Ts≈Tp. Here, the pressurization start timing Ts is close to 0.9 Tp, and pressurization is started shortly before the pressure wave returns to the pressurization chamber 14 and the indoor hydraulic pressure becomes maximum, and the pressurization is started at least under pressure. It is maintained until the time (Tp) at which the pulsation becomes maximum, and at this time Tp, the pressure applied to the internal liquid by the drive unit 16 is controlled to be sufficiently large (see FIG. 2). As can be understood from FIG. 3, the indoor liquid whose turbulence is increased in this way is ejected from the nozzle 12 in a liquid yarn state, but after the ejection, the liquid yarn is broken to form droplets that are atomized. . In addition, the droplets discharged from the nozzle and atomized do not fly along the same path, and as shown in FIG. 4, the droplets do not coalesce even 20 mm downstream, and are present in the flight space at random. . The particle size of the droplets ejected from the nozzle 12 is 20 μm around the nozzle as shown in FIG. 3 and is 22 μm as shown in FIG. In addition, the state scattered in the space is maintained.

  As described above, in the liquid ejecting apparatus according to the present embodiment, it is difficult for the discharged droplets to coalesce by actively promoting disturbance of pulsation, and droplets having a small particle diameter are continuously generated from the nozzle 12. A plurality of liquids can be ejected, and the amount of liquid (flow rate) ejected from the nozzle 12 can be increased.

  FIG. 5 is a photograph of the state of droplets ejected by a control method employed in a conventional inkjet technology in the so-called printing field. Except for the control of the pressurization timing, the used liquid ejecting apparatus and discharged liquid are the same as the apparatus and liquid according to the above-described embodiment. In the conventional ink jet technology, liquid droplets are ejected by extruding liquid in a flow channel one by one from a nozzle. Since it is necessary to discharge droplets having the same particle diameter continuously and stably in the printing operation, the drive unit that pressurizes the liquid is controlled so that the liquid in the flow path is less disturbed as much as possible.

  In the example of FIG. 5, actually, the pressurization start timing Ts is set to Ts≈1.5 Tp, and droplets are ejected from the nozzle at a cycle of 50 kHz. The droplet velocity in the vicinity of the nozzle outlet shown in FIG. 5A is 11.09 m / s and the particle size is 18 μm. The droplets 1 mm to 10 mm downstream from the nozzle are as shown in FIG. In addition, the particle size exceeds 30 μm. That is, the particle size is approximately doubled by 10 mm downstream (merged three times). In printing applications, since the distance to the paper on which the ejected droplets land is short, coalescence between the ejected droplets does not occur, but it is used in a fuel injection device for automobiles as described later to fly a long distance. Then, coalescence of the droplets downstream occurs.

  6 shows the conventional pressurization timing (Ts≈1.5Tp) shown in FIG. 5 and the pressurization timing (Ts≈Tp, more specifically Ts ≦ Tp) of the present embodiment shown in FIG. Shows the relationship between the distance from the nozzle and the average particle diameter. In the case of the conventional control method, as apparent from FIG. 6, the average particle diameter of the droplets is about 18 μm near the nozzle outlet (distance 0), but the average particle diameter rapidly increases until it reaches 10 mm. Continuing to expand, it is about 38 μm at 10 mm, more than twice. On the other hand, in the case of the pressurization timing of the present embodiment as shown in FIG. 2, even when the distance from the nozzle is 10 mm and 20 mm, the increase degree of the average particle diameter of the droplet is very low from FIG. Is also obvious. In addition, since the droplet size variation is small and droplets having a uniform particle size in the range of 20 μm to 30 μm can be obtained, the fuel efficiency can be improved by using it as an engine liquid fuel injection device as described later. It becomes possible to contribute to improvement and improvement of purification of exhaust gas.

  7 to 9 are the same conditions as those of the liquid ejecting apparatus according to the present embodiment described above. For comparison, the pressurization period T of the indoor liquid by the drive unit is 0.35 Tp, 0.5 Tp, and 1.25 Tp. It is the figure which image | photographed the mode of the droplet discharged from the nozzle at the time of doing. FIG. 7 shows a case where Ts = 0.35Tp (Ts <0.5), the acceleration is not sufficient, and the droplet velocity ejected from the nozzle is 0.3 m / s, and the ejection velocity is small. In addition, the flight directions of the droplets are the same. Therefore, it can be understood that droplets are already likely to coalesce at the nozzle outlet.

  FIG. 8 shows a case where Ts = 0.5 Tp, and droplets ejected from the nozzles fly in the same direction as in FIG. 7 and fly at very close intervals although they are equally spaced in the figure. is doing. On the other hand, as apparent from the comparison with FIG. 7, the particle diameter of each droplet is highly uniform, but the average particle diameter is large. The droplet velocity is 1.04 m / s, which is larger than that in the case of Ts = 0.35 Tp, but the acceleration is not sufficient. Therefore, coalescence occurs when flying over a long distance, resulting in a large droplet size, and it is difficult to eject a large amount of liquid.

  FIG. 9 shows a case where Ts = 1.25 Tp, and the droplets ejected from the nozzle are smaller than those in FIG. 7, and there is slight variation in the flight direction, but droplet coalescence is occurring. That is confirmed. For this reason, it can be understood that further coalescence occurs while the droplets fly longer than the illustrated position. The droplet velocity is 4.56 m / s, which is higher than the case of Ts = 0.35 Tp and 0.5 Tp shown in FIGS. 7 and 8, but is not suitable for a large amount of ejection. .

  As described above, it can be seen that, under the conditions of Ts ≦ 0.5 Tp and Ts> Tp, the ejected droplets are not suitable for applications that require flying over a long distance with a small particle size. It can also be seen that a sufficient droplet velocity (ejection velocity) cannot be obtained, which is not suitable for spraying a large amount of liquid uniformly into the space.

  FIG. 10 shows a schematic configuration example of an internal combustion engine 10 that uses the liquid injection device according to the present embodiment as a liquid fuel injection device. In this internal combustion engine, a liquid fuel injection device 102 according to this embodiment for injecting liquid fuel is provided near the intake port of the intake pipe 120.

  The liquid fuel injection device 102 is supplied with the fuel pumped from the fuel tank 160 by the pump 162, and more specifically, to the common liquid chamber 20 shown in FIG. 1 of the fuel injection device 102 via the pump 162. Liquid fuel is supplied from the fuel tank 160. In addition, in the conventional fuel injection device, a pressurizing pump is necessary. However, in the present embodiment, since the necessary pressurization is performed in the pressurizing chamber, it is necessary to supply the common liquid chamber 20 with the pressurized liquid. The pump 162 is small and does not require a pressurizing function, and a small pump 162 can be employed.

  An ignition plug 140, an intake valve 124, and an exhaust valve 126 are provided in the vicinity of the upper portion of the cylinder 110, and a piston 114 that moves up and down along the cylinder axis and is connected to the crankshaft by a connecting rod is provided in the cylinder 110. Is provided. The intake pipe 120 is provided with a throttle valve 122 to control the intake air amount of the cylinder 110. The throttle valve 122 is provided with an air flow meter (not shown) that measures the flow rate of air passing through the valve and outputs an air flow meter signal. Further, the exhaust port of the cylinder 110 is connected to the exhaust pipe 130, and an exhaust catalyst 128 made of a three-way catalyst or the like is installed at the end. The ECU 150 controls the liquid fuel injection amount, the air amount, the ignition timing, and the like, and also controls the pressurization timing in the drive unit of the fuel injection device according to the present embodiment.

  Here, the general diameter of the intake pipe 120 is about 20 to 30 mm in radius, and the liquid injection apparatus 100 according to this embodiment is used as the fuel injection apparatus 102 to inject fuel into the intake pipe 120. Thus, in the intake pipe 120, the injected liquid fuel droplets can be dispersed with a fine particle size without coalescence. Therefore, the miscibility with air is good, and the fuel efficiency of the internal combustion engine can be improved. In addition, since droplets having a uniform and fine particle diameter can be mixed with air, incomplete combustion can be reduced, and the exhaust can be cleaned. Further, as the liquid fuel injection device 102, a device in which a plurality of nozzles are arranged in parallel can be used, and liquid fuel can be injected from the injection device 102 that is two-dimensionally arranged in the intake port. Therefore, a required amount of liquid fuel can be injected into the intake port using the surface, and the liquid injection device can be reduced in weight and thickness (reduction in depth).

  In the drive unit of the fuel injection device 102, when the piezo element or the heating element fluctuates in the pressure applied to the internal liquid due to the temperature change or change over time, the characteristic fluctuation is mapped in the ECU 150 in advance, The driving conditions such as the driving time and driving timing of the element can be controlled in accordance with the change in element characteristics. By such control, the pressurization start timing Ts for the internal liquid in the pressurization chamber can be set to actually satisfy 0.5Tp <Ts ≦ Tp.

  Further, the applied pressure in the drive unit may be controlled in accordance with the pressure fluctuation at the nozzle outlet of the fuel injection device 102, that is, the intake pipe port. In this case, for example, a pressure sensor may be provided in the intake pipe 120, and the ECU 150 may control the voltage applied to the element of the drive unit, the application time, the voltage, and the like according to the detected pressure.

  Although the fuel injection device 102 is installed above the intake pipe 120 in FIG. 10, it may be provided on the lower side. Further, the intake pipe 120 may be provided with a recovery unit that recovers the liquid fuel and makes the fuel injection device 102 or the tank 160 via a filter or the like. The recovery unit may recover the liquid fuel remaining in the intake pipe 120 without being mixed with air even when discharged from the fuel injection device 102. In addition, in order to prevent clogging at the nozzle of the fuel injection device 102 or to eliminate clogging, when liquid in the chamber is pressurized and injected from the nozzle during nozzle cleaning, excess liquid fuel is generated. However, it can also be recovered. However, when the liquid fuel is injected from the nozzle, even if the nozzle outlet is wet with the liquid fuel, the liquid fuel that has wetted the nozzle outlet when the liquid fuel continues to be injected from the nozzle is also contained in the intake pipe 120 as a droplet. The recovery unit is not essential because the nozzle can be sprayed and dried.

It is a figure which shows schematic structure of the liquid ejecting apparatus which concerns on embodiment of this invention. It is a figure which shows the pressurization control method in the liquid ejecting apparatus which concerns on embodiment of this invention. It is the figure which image | photographed the mode of the droplet of the nozzle exit vicinity at the time of controlling the liquid ejecting apparatus which concerns on this embodiment. It is the figure which image | photographed the mode of the droplet 20 mm downstream from the nozzle of the droplet of FIG. It is the figure which image | photographed the mode of the droplet discharged from the liquid ejecting apparatus by the conventional control method. FIG. 6 is a diagram illustrating a relationship between a distance from a nozzle and an average particle diameter of droplets in the case of the pressure control in FIG. 5 and the pressure control in FIG. 2 in the liquid ejecting apparatus. It is the figure which image | photographed the mode of the droplet of the nozzle exit vicinity when pressurization start timing Ts was 0.35 Tp in the liquid ejecting apparatus. It is the figure which image | photographed the mode of the droplet near a nozzle exit when the pressurization start timing Ts is 0.5 Tp in a liquid ejecting apparatus. It is the figure which image | photographed the mode of the droplet of the nozzle exit vicinity when the pressurization start timing Ts was set to 1.25Tp in a liquid ejecting apparatus. It is a figure which shows the example of schematic structure of the internal combustion engine using the liquid injection device which concerns on this embodiment as a fuel injection device.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 Internal combustion engine, 12 Nozzle, 14 Pressurization chamber, 16 Drive part, 18 Fluid resistance part, 20 Common liquid chamber, 100 Liquid injection device, 102 Fuel injection device, 110 Cylinder, 114 Piston, 120 Intake pipe, 122 Throttle valve, 124 intake valve, 126 exhaust valve, 128 exhaust catalyst, 130 exhaust pipe, 160 fuel tank, 162 pump.

Claims (5)

A liquid ejecting apparatus that ejects liquid from a nozzle,
A pressurizing chamber that communicates with the nozzle and has a drive unit that pressurizes the liquid in the chamber;
The pressure pulsation cycle applied to the liquid in the pressurizing chamber by the drive unit is represented by Tp, the pressure pulsation speed is represented by V, and the pulsation movement distance corresponding to the distance from the drive unit to the nozzle is represented by L. The pulsation period Tp is equal to 2 L / V,
The drive unit is
0.5Tp <Ts ≦ Tp
Pressurizing the indoor liquid at a pressurization start timing Ts satisfying
A liquid ejecting apparatus that ejects liquid from the nozzle.   2. The liquid ejecting apparatus according to claim 1, wherein the liquid is a liquid fuel for an internal combustion engine, and the liquid fuel ejected from the nozzle is supplied to the cylinder. A liquid fuel injection device for injecting liquid fuel from a nozzle and supplying the liquid fuel to a cylinder,
A pressurizing chamber that communicates with the nozzle and has a drive unit that pressurizes liquid fuel in the chamber;
The drive unit pressurizes the indoor liquid fuel at a timing that disturbs the pulsation of the pressure generated in the indoor liquid fuel in the pressurizing chamber,
A liquid fuel injection device for injecting liquid fuel from the nozzle. A liquid fuel injection device for injecting liquid fuel from a plurality of nozzles and supplying the liquid fuel to a cylinder,
A common liquid chamber that is common to the plurality of nozzles and stores the liquid fuel;
A pressurizing chamber that communicates with corresponding nozzles of the plurality of nozzles and has a drive unit that pressurizes liquid fuel in the chamber;
A fluid resistance path for communicating the common liquid chamber and the corresponding pressurizing chamber, and supplying the required amount of liquid fuel from the common liquid chamber to the pressurizing chamber;
Have
The drive unit pressurizes the indoor liquid fuel at a timing that disturbs the pulsation of the pressure generated in the indoor liquid fuel in the pressurizing chamber,
A liquid fuel injection apparatus, wherein liquid fuel is injected from the corresponding nozzle. In the liquid fuel injection device according to claim 3 or 4,
When the pulsation cycle of the pressure applied to the indoor liquid in the pressurizing chamber by the drive unit is represented by Tp, the pressure pulsation speed V, and the pulsation movement distance corresponding to the distance from the drive unit to the nozzle by L, The pulsation period Tp is equal to 2 L / V,
The drive unit is
0.5Tp <Ts ≦ Tp
Pressurizing the indoor liquid fuel at a pressurization start timing Ts satisfying
A liquid fuel injection apparatus, wherein liquid fuel is injected from the corresponding nozzle.