CN114017224A - Noise reduction structure for reducing fuel pulsation excitation force based on damping holes - Google Patents

Noise reduction structure for reducing fuel pulsation excitation force based on damping holes Download PDF

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Publication number
CN114017224A
CN114017224A CN202111464076.6A CN202111464076A CN114017224A CN 114017224 A CN114017224 A CN 114017224A CN 202111464076 A CN202111464076 A CN 202111464076A CN 114017224 A CN114017224 A CN 114017224A
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CN
China
Prior art keywords
injector
fuel
orifice
common rail
oil
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Pending
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CN202111464076.6A
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Chinese (zh)
Inventor
田绍军
杨丽
曾庆懿
钟柱声
赵钪
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SAIC GM Wuling Automobile Co Ltd
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SAIC GM Wuling Automobile Co Ltd
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Application filed by SAIC GM Wuling Automobile Co Ltd filed Critical SAIC GM Wuling Automobile Co Ltd
Priority to CN202111464076.6A priority Critical patent/CN114017224A/en
Publication of CN114017224A publication Critical patent/CN114017224A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/09—Fuel-injection apparatus having means for reducing noise

Abstract

The invention discloses a noise reduction structure for reducing fuel pulsation exciting force based on a damping hole, which comprises: at least one damping hole is arranged on an oil outlet pipeline between each cylinder oil injector of the engine and the common rail pipe; alternatively, at least one orifice is provided in the outlet line between the particular engine cylinder injector and the common rail. The technical scheme of the invention attenuates the impact energy of high-pressure transient fuel on the common rail pipe from the source, eliminates vibration noise, and has the advantages of simple structure, low cost, small change and easy production and manufacture.

Description

Noise reduction structure for reducing fuel pulsation excitation force based on damping holes
Technical Field
The invention relates to a vibration reduction and noise reduction technology of an oil supply system of an internal combustion engine, in particular to a noise reduction structure for reducing fuel pulsation exciting force based on a damping hole.
Background
With the improvement of the performance of the oil injector and the use of multiple injection and lean combustion technologies, the fuel pressure is improved, the single injection pulse width is shortened, the closing time of the needle valve of the oil injector is shortened, and the water hammer effect after the needle valve of the oil injector is closed is increased. Water shock waves are transmitted in a pipe-containing system between an oil injector needle valve and a high-pressure oil pump, the pressure and the speed of oil in the pipe-containing system are changed alternately, impact vibration radiation noise is formed on a structure, the water shock waves are transmitted to the needle valve of the oil injector of each cylinder, the pressure fluctuation at the needle valve is increased, the fuel injection stability and the atomization performance are influenced, even serious people can cause the problems of uneven oil injection of each cylinder and each time of the engine, uneven cylinder pressure, increased engine output torque fluctuation, increased vibration noise, increased oil consumption, substandard emission and the like. Meanwhile, the length of the pipeline structure is short, the modal frequency of the pipeline structure is high, the water shock wave frequency is high, the frequency of the structural vibration radiation noise is within the range of the sensitive frequency band of human ears and is unsteady intermittent knocking sound, and the noise quality and riding comfort of a vehicle are influenced.
In the prior art, the problems of fuel pulsation of an internal combustion engine oil supply system and vibration noise caused by the fuel pulsation are solved by the following method measures and structural forms:
1. for example, patent publication nos. CN105927386A, CN20811073U, CN208153160U and CN208816260U disclose technical solutions, a sound absorption and insulation part is wrapped outside the oil supply system pipeline, and the sound absorption and insulation part generally adopts a high-low density composite non-metallic structural member. The problem is that the assembly on the engine can affect the heat diffusion of the engine; in addition, the parts have larger structural size, need to occupy larger space, have larger weight and higher cost. In addition, the structure can only reduce partial noise energy radiated by vibration of the oil supply system pipeline, is low in efficiency, has no effect on the noise of the oil supply system structure which is transmitted into the vehicle by vibration, and has no effect on a series of problems related to instability of oil injection quantity caused by fuel pressure pulsation and speed pulsation impact.
2. In the technical solutions disclosed in patent publications CN103410644A and CN105840373B, one or more elastic and damping elements are connected in series to an oil inlet line of an oil rail or an oil outlet line between a common rail and an injector to reduce or eliminate fuel pulsation and vibration noise caused by the fuel pulsation. The structure has the disadvantages that at least 1 joint is added on the pipeline, the risk of fuel leakage is increased, and the reliability is reduced; moreover, if the additional elastic damping element fails, the oil supply of the internal combustion engine is not smooth, and the faults of insufficient acceleration, shaking, even flameout and shutdown and the like occur; in addition, the used elastic damping element is generally large in structural size, needs to occupy a certain space, is complex in structure and is high in cost; the elastic damping element is generally made of non-metallic materials, failure modes such as foaming and mechanical property change are easy to occur after the elastic damping element is soaked in high-temperature and high-pressure fuel oil for a long time, and oil circuit faults are easy to cause after the elastic damping element is failed.
3. In the solutions disclosed in patent publications US7341045B2, US9518544B2 and US20060081220a1, an elastic damping element is arranged in the oil rail. The structure has the problems of complex structure, high requirement on manufacturing process, large structural size, occupation of a large part of space in the common rail pipe and high manufacturing cost.
4. In the technical scheme disclosed in patent publication No. CN210919300U, a plurality of small partition holes are arranged on the cross section of the common rail pipe, so that the hydraulic impact energy is reduced. The oil rail processing device has the problems that the processing difficulty is high, and the oil rail processing device is not suitable for processing and forming of an integrated machine.
5. In the technical scheme disclosed in the patent publication number of US8402947B2, based on the design concept of acoustic cavity resonance and acoustic cavity mode vibration mode excitation point avoidance, the common rail pipe partition is divided into a plurality of cavities, the acoustic cavity modes of all cavities of the common rail pipe are improved, oil outlet pipe orifices of all cylinders are located at acoustic cavity nodes, and the water hammer excitation response of the acoustic cavity modes is reduced. The structure arranges a plurality of partitions in the common rail pipe, has larger manufacturing and processing difficulty and is not suitable for integrally machining the common rail pipe.
Disclosure of Invention
In order to overcome the problems in the prior art, the invention provides a noise reduction structure for reducing fuel pulsation excitation force based on damping holes, so that the impact energy of high-pressure transient fuel on a common rail pipe is attenuated from the source, and vibration noise is eliminated.
A noise reduction structure for reducing fuel pulsation excitation force based on damping holes comprises:
at least one damping hole is arranged on an oil outlet pipeline between each cylinder oil injector of the engine and the common rail pipe; alternatively, at least one orifice is provided in the outlet line between the particular engine cylinder injector and the common rail.
Optionally, the oil outlet pipeline further comprises an oil injector seat; the common rail pipe is connected with the oil injector base and forms the oil outlet pipeline; a bushing with a damping hole is assembled between the common rail pipe and the injector seat;
optionally, the bushing is in interference fit with the injector seat;
optionally, after the bushing is pressed into a counter bore on the injector seat, the common rail pipe is welded with the injector seat through brazing materials;
optionally, the oil outlet pipeline further comprises an oil injector seat, and the oil injector seat is connected with the common rail pipe to form the oil outlet pipeline; at least one damping hole is arranged on an inner flow passage of the oil injector seat;
optionally, the oil outlet pipeline further comprises an oil injector seat, and an oil outlet hole is formed in an internal flow channel of the common rail pipe; the oil injector seat is connected with the oil outlet hole and forms the oil outlet pipeline; at least one damping hole is arranged on the oil outlet hole;
optionally, the specific engine cylinder fuel injector comprises a first cylinder and/or a third cylinder and a fourth cylinder fuel injector;
optionally, the fuel injector further comprises a fuel injector needle valve, and the fuel injector seat is located between the fuel injector needle valve and the common rail pipe;
optionally, the diameter of the damping hole is between 0.5 and 2.5 mm;
optionally, the length of the damping hole is between 0.5 and 30 mm.
According to the noise reduction structure for reducing the fuel pulsation exciting force based on the damping hole, the appropriate damping hole is arranged on the oil outlet pipeline between the common rail pipe and the oil sprayer, so that a good impedance effect is achieved on the high-frequency conversion water shock pressure wave and the high-frequency reversing transient flow speed after the oil sprayer is closed, meanwhile, the local pressure loss and the on-way pressure loss of the normally low-speed flowing fuel are small, and the influence on the flow is negligible; therefore, impact energy of high-pressure transient fuel on the common rail pipe is attenuated from the source, and vibration noise is eliminated.
The pipeline runner structure can be realized only by properly optimizing the pipeline runner structure, and the pipeline runner structure is simple in structure, low in cost, small in change, easy to produce and manufacture and suitable for changing the existing integrated pipeline and split type support. In addition, the water shock wave energy is consumed by increasing the local impedance through changing the cross section structure of the flow passage, additional functional parts are not required to be added, and the reliability of the pipeline system is improved.
Compared with the prior art, the scheme can effectively attenuate the pulsation energy of the fuel in the fuel supply pipeline of the internal combustion engine, and reduce and eliminate a series of side effects caused by fuel pressure and speed pulsation, such as unstable fuel injection quantity of each cylinder, uneven cylinder pressure, rough engine operation, high vibration noise, pipeline cavitation, high pipeline vibration noise and the like.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the description of the embodiments of the present invention will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art that other drawings can be obtained according to these drawings without inventive labor.
FIG. 1 is a schematic diagram of a noise reduction structure for reducing fuel pulsation excitation force based on damping holes according to an embodiment of the present invention;
FIG. 2 is a partial enlarged view of a noise reduction structure for reducing fuel pulsation excitation force based on damping holes according to an embodiment of the present invention;
FIG. 3 is a schematic diagram of a noise reduction structure for reducing fuel pulsation excitation force based on damping holes according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of a noise reduction structure for reducing fuel pulsation excitation force based on damping holes according to another embodiment of the present invention;
FIG. 5 is a partial enlarged view of a noise reduction structure for reducing fuel pulsation excitation force based on damping holes according to another embodiment of the present invention;
FIG. 6 is a schematic diagram of a noise reduction structure for reducing fuel pulsation excitation force based on damping holes according to another embodiment of the present invention;
FIG. 7 is a partial enlarged view of a noise reduction structure for reducing fuel pulsation excitation force based on orifice holes according to another embodiment of the present invention;
FIG. 8 is a partial enlarged view of a noise reduction structure for reducing fuel pulsation excitation force based on orifice holes according to another embodiment of the present invention;
FIG. 9 is a cross-sectional view of the flow path of the common rail to the injector needle in an embodiment of the present invention;
FIG. 10 is a graph of rail tip water hammer pressure waves as a function of orifice diameter for an embodiment of the present invention;
FIG. 11 is a diagram of measured values of pressures before and after a rapid acceleration damping orifice in an embodiment of the present invention;
FIG. 12 is a mode diagram of a1 st order acoustic cavity for fuel without damping holes;
FIG. 13 is a modal diagram of a fuel-1 st order acoustic cavity with damping holes in an embodiment of the present invention;
the reference numbers in the drawings of the specification are as follows:
100. a common rail pipe; 200. a bushing with a damping hole; 300. an oil sprayer seat; 400. brazing solder; 500. a damping hole; 1. a common rail pipe; 2. an oil outlet pipe; 3. water shock waves passing through the damping holes; 4. a damping hole; 5. an oil outlet pipe; 6. water shock waves passing through the damping holes; 7. a needle valve of the oil injector, 8 and an oil inlet pipe.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, not all, embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The invention provides a noise reduction structure for reducing fuel pulsation exciting force based on damping holes, wherein at least one damping hole with a smaller diameter is designed on an oil outlet pipeline between each cylinder fuel injector and a common rail pipe; or at least one damping hole with a small diameter is designed on the oil outlet pipeline between the cylinder oil injector and the common rail pipe. For example, at least one damping hole with a small diameter is designed in the oil outlet pipeline between the 1 st cylinder and (or) the 3 rd cylinder and the 4 th cylinder oil injectors and the common rail pipe with a strong water hammer effect.
On the premise of not influencing normal flow and meeting the pressure loss requirement, the diameter and the length of the damping hole are flexibly adjusted according to the actual effect, the diameter of the damping hole is generally between 0.5mm and 2.5mm, and the length of the damping hole is generally between 0.5mm and 30 mm.
Among them, the most influential to the knocking vibration noise is the orifice diameter. According to different parameters of an oil supply pipeline system and different water hammer effects, the diameter is designed to be proper and needs to be smaller than a certain value, the specific value is determined by tests or calculation, the flow and pressure requirements are met, and the knocking sound inside and outside the vehicle can be effectively eliminated.
Secondly, what has an effect on the knocking vibration noise is the length of the damping hole, and the length design of the damping hole mainly considers the processing performance and the influence on the pressure loss and the flow. .
As shown in fig. 1, 2 and 3, in one embodiment, a bushing 200 with a damping hole is assembled between the common rail pipe 100 and the injector seat 300 (oil outlet pipe structure) between the injector needle valves of each cylinder (a certain cylinder), the bushing and the injector seat are in interference fit, the damping hole bushing is pressed into a counter bore on the injector seat, and then the common rail pipe and the injector seat are welded by brazing material 400. Further, the damping hole in the bushing 200 with the damping hole has a thin shell structure as shown in fig. 2 when the length of the damping hole is small, and the damping hole has a solid structure with the length of the damping hole equal to the length of the bushing when the length of the damping hole is large. The bushing 200 has the functions of welding positioning and preventing brazing solder from infiltrating into the damping hole after melting.
Further, in one embodiment, as shown in fig. 4 and 5, at least one orifice 500 is provided in the inner flow path of the injector mount between the common rail and the injector needle of each cylinder (cylinder). Compared with the first embodiment, the structure does not need to additionally increase a damping hole bushing, but is directly processed on the oil injector seat, so that the process is simple and the cost is lower.
Further, in one embodiment, as shown in fig. 6, 7 and 8, a damping hole 500 is provided in the oil outlet hole connecting the injector seat of each cylinder (a certain cylinder) and the internal flow passage of the common rail pipe. Compared with the first embodiment, the structure does not need to additionally increase a damping hole bushing, but is directly processed on the common rail pipe, so that the process is simple, and the cost is lower.
For ease of understanding, the working principle of the present damping hole based noise reduction structure is as follows, as shown in fig. 9:
the fuel supply system of the internal combustion engine comprises a power element and a valve, wherein the power element works in a pulse mode, such as an oil pump, a one-way valve and an oil injector, and the valve works in an opening and closing mode, and the flowing state of the fuel can be changed suddenly in the flowing process, so that certain pressure pulsation and speed pulsation, including violent pressure pulsation and speed pulsation such as water shock waves (hydraulic shock) and the like, exist in the fuel in the flowing process; the fuel pulsation causes vibration noise, and the fuel pulsation causes unstable operation of the machine, performance degradation, damage to a pipeline of an oil supply system, and other failures. Therefore, there is a need to reduce or eliminate a number of side effects caused by fuel pressure and velocity pulsations.
Based on this, after the damping hole is arranged, the speed of the fuel oil flowing through the damping hole is increased, the speed gradient is increased, the friction damping is increased, the damping hole and the pipeline expansion cavity at the upper and lower positions of the damping hole form a region with a sudden change in section, the local resistance of the fuel oil is increased, and the pulsating flow energy of the fuel oil is reduced.
In fig. 9, after a certain cylinder needle valve 7 is opened to be closed, the upstream water shock wave oscillates between the needle valve 7 and the outlet of the common rail pipe 1 for one cycle, and the cycle can be divided into 4 stages: pressurization counter wave, decompression consequent wave, decompression counter wave and pressurization consequent wave.
In the stage of pressurization reverse wave, the water hammer wave is propagated to the position 3 from the position 6 through the damping hole 4, and because of the damping attenuation of the damping hole 4 and the reflection action caused by the section difference of the damping hole 4 and the oil outlet pipe 5, the energy of the water hammer wave after being propagated to the position 3 is greatly attenuated, the exciting force of the water hammer wave on the common rail pipe 1 structure and the sound cavity mode in the common rail pipe 1 can be effectively reduced, and therefore the vibration noise caused by the water hammer wave is reduced or eliminated.
Similarly, energy attenuation occurs when the water shockwave travels in a reverse direction from the flowline 2 through the damping holes 4 to the flowline 5. Oil injectionThe distance between the needle valve and the common rail pipe is l, and when a certain cylinder oil sprayer sprays oil, the pressure in the oil outlet pipe after the needle valve is opened is p0Flow velocity of + v0The needle valves of the oil injectors of other cylinders and the high-pressure oil pump oil outlet one-way valves on the oil inlet pipes are closed, the length and the volume of the common rail pipe are large, and the common rail pipe, the oil outlet pipe and the oil inlet pipe which do not inject oil can be regarded as a closed container. According to the takowski water shock wave process, the oscillation of the upstream water shock wave between the valve and the pipeline inlet after the valve of a certain cylinder is opened to be closed can be divided into 4 stages: pressurization counter wave, decompression consequent wave, decompression counter wave and pressurization consequent wave.
Due to inertia and compressibility of the fuel, the fuel velocity + v in the cylinder tube after the needle valve is closed0The pressure from the needle valve of the oil injector to the interface of the oil outlet pipe and the common rail pipe is reduced to 0 in sequence, and the pressure is reduced from p0Increase to p in turn0+ΔpAt time l/c, the fuel speed in the whole pipeline is changed to 0, and the pressure is changed to p0+ΔpThis is the 1 st stage of water hammer wave propagation, called the supercharging counter wave.
The 2 nd stage decompression parawave is caused by the fact that the pressure in the cylinder outlet pipe is higher than the pressure in the common rail pipe by deltapThe fuel oil in the oil outlet pipe expands under the action of pressure difference and flows back to the common rail pipe, and the speed of the fuel oil in the oil outlet pipe is reversely increased from a pipe orifice to a needle valve from 0 to-v0Pressure is from p0+ΔpReduced to p0。
The 3 rd stage is decompression reverse wave, the fuel oil in the oil outlet pipe continuously flows out due to the inertia effect, the valve is cut off, and the speed is controlled from-v0Decreasing to 0 and pressure from p0Reduced to p0-Δp。
The 4 th stage is pressurization following wave, and when the pressure in the common rail pipe is higher than the pressure in the oil outlet pipe at the 3l/c moment, under the action of the pressure difference, the fuel oil enters the pipe again, and the speed in the pipe is recovered to + v from 00Pressure is from p0-ΔpRestore to p0And when the fuel state in the pipe and the deformation of the pipe are recovered to the valve closing time at the time of 4l/c, repeating the 4 stages.
Frequency f of water shock wave is c/4l, size of water shock wave crest is deltapWith fuel qualityThe volume, momentum and speed change are related to the water shock wave speed c, which is related to the elastic modulus of the pipe wall material, the pipe wall thickness, the fluid bulk modulus and the sound velocity and changes with the pressure and temperature change.
As shown in fig. 10, the length and diameter of the damping hole in the fuel oil pipeline of the three-cylinder engine are not changed, and the water hammer pressure value at the axle center of the end part of the common rail pipe is compared, which is calculated by adopting a numerical simulation method and under the solution of the noise reduction structure of the present invention.
As can be seen from FIG. 10, the maximum value of the water hammer pressure wave without the damping hole reaches 2.35 MPa; when the diameter of the damping hole is 1.0mm, the maximum pressure wave is reduced to 0.22MPa, which is 9.4% of that of the damping hole without the damping hole. That is, with a damping orifice, the water hammer pressure wave decays very fast, and without a damping orifice, the pressure wave decays very slowly. Impact is formed on the pipeline structure when the water hammer pressure waves are changed alternately, and the impact force is in direct proportion to the water hammer pressure waves; therefore, the damping orifice diameter needs to be controlled below a certain value to reduce the water hammer vibration noise to an acceptable level. The damping hole with reasonable design only has good impedance effect on high-frequency conversion water shock pressure waves and high-frequency reversing transient flow speed after the fuel injector needle valve is closed, has small local pressure loss and on-way pressure loss of normally low-speed flowing fuel, and has negligible influence on flow.
As shown in figure 11, the loading of the damping hole measures the pressure value of 0 Hz-1000 Hz before and after the damping hole, the diameter of the damping hole is 1.3mm, the length is 2mm, the 90-degree right-angle transition is carried out, the working condition is idle neutral position rapid acceleration, and the pressure loss before and after the damping hole is not more than 0.2 MPa.
The modal calculation analysis of the fuel oil acoustic cavity of the oil rail assembly (comprising an oil inlet pipe and oil outlet pipes of each cylinder) with the four-cylinder machine without damping holes is carried out, the damping holes do not change the modal vibration mode of the whole fuel oil acoustic cavity, only the modal frequency is reduced, and the modal frequency is reduced from 1696Hz to 1671 Hz. As shown in fig. 12, it is a mode diagram of a1 st order acoustic cavity of fuel without damping holes; fig. 13 is a modal diagram of a sound cavity of step 1 of fuel with a damping hole according to an embodiment of the present invention. As can be seen from the comparison of fig. 12 and 13, the 1 st order acoustic node is still located in the middle of the common rail pipe, and the position of the modal node of the acoustic cavity of the pipe system is not changed by the action of the damping hole located between the common rail pipe and the injector needle valve, so that the acoustic-solid coupling effect is reduced to reduce the vibration noise; before the water shock wave enters the common rail pipe, the water shock wave energy is attenuated by using the impedance effect, and the water shock wave pressure in the common rail pipe is reduced. Compared with the prior art, the technical scheme that a plurality of partition blocks with small holes are additionally arranged in the common rail pipe to change the position and the mode of the mode node of the common rail pipe sound cavity and improve the mode frequency of the sound cavity to reduce vibration and noise is essentially different.
The above-mentioned embodiments are only used for illustrating the technical solutions of the present invention, and not for limiting the same; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; such modifications and substitutions do not substantially depart from the spirit and scope of the embodiments of the present invention, and are intended to be included within the scope of the present invention.

Claims (10)

1. The utility model provides a structure of making an uproar falls of reduction fuel pulsation exciting force based on damping hole which characterized in that includes:
at least one damping hole is arranged on an oil outlet pipeline between each cylinder oil injector of the engine and the common rail pipe; alternatively, at least one orifice is provided in the outlet line between the particular engine cylinder injector and the common rail.
2. The orifice-based noise reducing structure for reducing fuel pulsation excitation force according to claim 1, wherein said outlet pipe further comprises an injector seat; the common rail pipe is connected with the oil injector base and forms the oil outlet pipeline; and a bushing with a damping hole is assembled between the common rail pipe and the injector seat.
3. The orifice-based noise reducing structure for reducing fuel pulsation excitation force according to claim 2, wherein said bushing is interference-fitted with said injector seat.
4. The orifice-based noise reducing structure for reducing the fuel pulsation excitation force according to claim 3, wherein the common rail pipe is welded to the injector seat by brazing after the bushing is pressed into the counter bore of the injector seat.
5. The orifice-based noise reducing structure for reducing fuel pulsation excitation force according to claim 1, wherein said outlet pipe further comprises an injector seat connected to said common rail pipe and forming said outlet pipe; and at least one damping hole is arranged on the inner flow passage of the injector seat.
6. The orifice-based noise reduction structure for reducing the fuel pulsation excitation force according to claim 1, wherein the oil outlet pipe further comprises an oil injector seat, and the oil outlet orifice is provided in the internal flow passage of the common rail pipe; the oil injector seat is connected with the oil outlet hole and forms the oil outlet pipeline; and at least one damping hole is arranged on the oil outlet hole.
7. The orifice-based noise reducing structure for reducing fuel pulsation excitation force according to claim 1, wherein the specific engine cylinder injector includes a first cylinder and/or a third cylinder and a fourth cylinder injector.
8. The orifice-based noise reducing structure for reducing the pulsating exciting force of fuel according to any of claims 2 to 7, wherein said fuel injector further comprises a fuel injector needle valve, and said fuel injector seat is located between said fuel injector needle valve and a common rail pipe.
9. The orifice-based fuel pulsation excitation force reducing noise reducing structure according to any one of claims 1 to 7, wherein the orifice has a diameter of 0.5 to 2.5 mm.
10. The orifice-based fuel pulsation excitation force reducing noise reducing structure according to any one of claims 1 to 7, wherein the length of the orifice is between 0.5 and 30 mm.
CN202111464076.6A 2021-12-03 2021-12-03 Noise reduction structure for reducing fuel pulsation excitation force based on damping holes Pending CN114017224A (en)

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Application Number Priority Date Filing Date Title
CN202111464076.6A CN114017224A (en) 2021-12-03 2021-12-03 Noise reduction structure for reducing fuel pulsation excitation force based on damping holes

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CN202111464076.6A CN114017224A (en) 2021-12-03 2021-12-03 Noise reduction structure for reducing fuel pulsation excitation force based on damping holes

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11241665A (en) * 1998-02-25 1999-09-07 Isuzu Motors Ltd Fuel injection device
JPH11241664A (en) * 1998-02-25 1999-09-07 Isuzu Motors Ltd Fuel injection device
CN210919300U (en) * 2019-10-25 2020-07-03 德尔福（上海）动力推进系统有限公司 Engine high-pressure oil rail with noise reduction throttle hole
CN112555077A (en) * 2020-12-03 2021-03-26 一汽解放汽车有限公司 Common rail pipe and diesel engine high-pressure oil supply system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11241665A (en) * 1998-02-25 1999-09-07 Isuzu Motors Ltd Fuel injection device
JPH11241664A (en) * 1998-02-25 1999-09-07 Isuzu Motors Ltd Fuel injection device
CN210919300U (en) * 2019-10-25 2020-07-03 德尔福（上海）动力推进系统有限公司 Engine high-pressure oil rail with noise reduction throttle hole
CN112555077A (en) * 2020-12-03 2021-03-26 一汽解放汽车有限公司 Common rail pipe and diesel engine high-pressure oil supply system

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